Vibration Assembly

Abstract

Disclosed is a vibration assembly (100), which includes an elastic element (110), which includes a central region (112), an edge region (114) disposed on the outer periphery of the central region (112), and a fixing region (116) disposed on the outer periphery of the edge region (114), and is configured to vibrate along a direction perpendicular to the central region (112), the central region (112) including an elastic member and a reinforcing member (120) laminated along the vibration direction, and the reinforcing member (120) has a plurality of groove structures (121) with openings facing the elastic member.

Description

[Technical field]

[0001] The present disclosure relates to the field of acoustics, and more particularly to vibrating assemblies.

[0002] [Incorporated by reference] This application claims priority to a Chinese application with application number 202211003675.2, filed on August 20, 2022, the entire contents of which are incorporated herein by reference. [Background technology]

[0003] A speaker usually includes three main parts: a driving part, a vibration part, and a supporting part. The vibration part is also the load part of the speaker, which is mainly a vibration assembly and includes an elastic element, such as a vibrating membrane. The vibration part is an important component of the speaker. When the driving force of the driving part is set, the vibration part can be reasonably designed so that the load part and the driving part can achieve good mechanical impedance matching, thereby achieving the output effect of high sound pressure level and wide bandwidth.

[0004] In vibration assemblies, a mass-rigidity structure made of metal such as aluminum alloy, stainless steel, titanium alloy, magnesium alloy, magnesium aluminum alloy, etc. is usually installed in the central region of the elastic element to improve the rigidity of the central region of the vibration membrane, and the cancellation of sound due to the split vibration mode in the range of 20 Hz to 20 kHz in the central region of the vibration membrane of the speaker can be avoided. However, if a mass-rigidity structure is directly installed in the central region of the elastic element, the mass of the entire vibration assembly increases, the load on the speaker increases, the impedance of the driving part and the load part becomes mismatched, and the sound pressure level output from the speaker decreases. Summary of the Invention [Problem to be solved by the invention]

[0005] Therefore, there is a need to provide a vibrating assembly in which a reinforcing member having a groove structure is rationally located in a central region of a resilient element. [Means for solving the problem]

[0006] A vibration assembly according to one embodiment of the present specification includes an elastic element including a central region, an edge region disposed on the outer periphery of the central region, and a fixed region disposed on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the central region including an elastic member and a reinforcing member stacked along the vibration direction, and the reinforcing member has a plurality of groove structures with openings facing the elastic member.

[0007] In some embodiments, the reinforcing member is provided with an openwork structure in areas other than the groove structure.

[0008] In some embodiments, the ratio of the projected area of ​​the reinforcing member to the projected area of ​​the central region in the vibration direction is in the range of 0.15 to 0.8.

[0009] In some embodiments, the ratio of the projected area of ​​the reinforcing member to the projected area of ​​the central region in the vibration direction is in the range of 0.35 to 0.65.

[0010] In some embodiments, the vibrating assembly, when vibrating, exhibits a resonant peak in the range of at least 10,000 Hz to 20,000 Hz.

[0011] In some embodiments, the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in a range of 7.14 or greater.

[0012] In some embodiments, the ratio of the height dimension to the thickness dimension is in the range of 9 or greater.

[0013] In some embodiments, the vibrating assembly, when vibrating, exhibits a resonant peak in the range of at least 5000 Hz to 10000 Hz.

[0014] In some embodiments, the groove structure has a height dimension along the vibration direction, the height dimension having a value in the range of 50 μm to 500 μm.

[0015] In some embodiments, the height dimension has a value in the range of 200 μm to 350 μm.

[0016] In some embodiments, a sidewall of the trench structure has a thickness dimension, the thickness dimension having a value in the range of 50 μm or less.

[0017] In some embodiments, the thickness dimension has a value in the range of 40 μm or less.

[0018] In some embodiments, an opening of the groove structure is provided with a skirt structure extending along a surface of the elastic member, the skirt structure having a width in the range of 100 μm to 300 μm.

[0019] In some embodiments, the width of the skirt structure is in the range of 100 μm to 200 μm.

[0020] In some embodiments, the shape of the groove structure comprises at least one of a U-shape, a T-shape, an L-shape, and a cone-shape.

[0021] In some embodiments, the Young's modulus of the material of the reinforcement member is higher than the Young's modulus of the material of the elastic member.

[0022] In some embodiments, the material of the reinforcement member is the same as the material of the elastic member.

[0023] In some embodiments, a filler material is disposed within the groove structure, the filler material having a Young's modulus less than the Young's modulus of a material of the reinforcing member.

[0024] A vibration assembly according to one embodiment of the present specification includes an elastic element including a central region, an edge region disposed on the outer periphery of the central region, and a fixed region disposed on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the central region including a reinforcing region and an elastic region arranged in parallel, and the reinforcing region has a plurality of groove structures with openings facing the vibration direction.

[0025] In some embodiments, the ratio of the projected area of ​​the reinforced region to the projected area of ​​the central region in the vibration direction is in the range of 0.15 to 0.8.

[0026] In some embodiments, the ratio of the projected area of ​​the reinforced region to the projected area of ​​the central region in the vibration direction is in the range of 0.35 to 0.65.

[0027] In some embodiments, the vibrating assembly, when vibrating, exhibits a resonant peak in the range of at least 10,000 Hz to 20,000 Hz.

[0028] In some embodiments, the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in a range of 7.14 or greater.

[0029] In some embodiments, the ratio of the height dimension to the thickness dimension is in the range of 9 or greater.

[0030] In some embodiments, the vibrating assembly, when vibrating, exhibits a resonant peak in the range of at least 5000 Hz to 10000 Hz.

[0031] In some embodiments, the groove structure has a height dimension along the vibration direction, the height dimension having a value in the range of 50 μm to 500 μm.

[0032] In some embodiments, the height dimension has a value in the range of 200 μm to 350 μm.

[0033] In some embodiments, a sidewall of the trench structure has a thickness dimension, the thickness dimension having a value in the range of 50 μm or less.

[0034] In some embodiments, the thickness dimension has a value in the range of 40 μm or less.

[0035] In some embodiments, an opening of the groove structure is provided with a skirt structure connected to the elastic region, the skirt structure having a width in the range of 100 μm to 300 μm.

[0036] In some embodiments, the width of the skirt structure is in the range of 100 μm to 200 μm.

[0037] In some embodiments, the shape of the groove structure comprises at least one of a U-shape, a T-shape, an L-shape, and a cone-shape.

[0038] In some embodiments, the Young's modulus of the material of the reinforced region is higher than the Young's modulus of the material of the elastic region.

[0039] In some embodiments, the material of the reinforced region is the same as the material of the elastic region.

[0040] In some embodiments, a filler material is disposed within the groove structure, the filler material having a Young's modulus smaller than the Young's modulus of a material of the elastic element.

[0041] The present specification will be further illustrated by exemplary embodiments, which are not limiting and will be described in detail with reference to the drawings, in which like numbers refer to like structures. [Brief description of the drawings]

[0042] [Figure 1] 1 is a schematic diagram of a vibrating assembly and its equivalent vibration model, according to some embodiments of the present disclosure. [Diagram 2]FIG. 13 illustrates a deformation diagram of a vibration assembly according to some embodiments herein at a first resonance peak. [Diagram 3] FIG. 13 is a deformation diagram of a vibration assembly according to some embodiments herein at a second resonance peak. [Figure 4] FIG. 13 is a deformation diagram of a third resonant peak of a vibration assembly according to some embodiments of the present disclosure. [Figure 5A] FIG. 2 is a frequency response curve diagram of a vibration assembly in accordance with certain embodiments of the present disclosure. [Figure 5B] FIG. 13 is a frequency response curve diagram for a vibration assembly according to some embodiments herein that does not have a third resonant peak. [Figure 6] 1 is a frequency response curve diagram of a vibration assembly including a groove structure and a vibration assembly without a groove structure, according to some embodiments of the present disclosure. [Figure 7A] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 7B] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 7C] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 7D] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 7E] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 7F] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 7G] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure. [Figure 8] FIG. 2 is a schematic diagram of a groove structure according to some embodiments of the present disclosure. [Figure 9]FIG. 13 is another frequency response curve diagram of a vibration assembly in accordance with certain embodiments of the present disclosure. [Figure 10] 13A-13C are frequency response curve diagrams of a vibrating assembly corresponding to stiffening members of different heights, in accordance with some embodiments herein. [Figure 11] 13A-13C are frequency response curve diagrams of a vibrating assembly corresponding to stiffening members of different thicknesses, in accordance with some embodiments herein. [Figure 12] 2 is a schematic diagram of a skirt structure according to some embodiments herein. [Figure 13] 11A-11C are frequency response curve diagrams of a vibrating assembly corresponding to stiffening members with different skirt structure widths, in accordance with some embodiments herein. [Figure 14A] 2A to 2C are schematic diagrams illustrating a manufacturing process of a non-metallic reinforcing member according to some embodiments of the present disclosure. [Figure 14B] FIG. 14B is a schematic diagram of a model corresponding to FIG. 14A. [Figure 15A] 1A to 1C are schematic diagrams illustrating a manufacturing process of a metallic reinforcing member according to some embodiments of the present specification. [Figure 15B] FIG. 15B is a schematic diagram of a model corresponding to FIG. 15A. [Figure 16] 1 is a schematic diagram of a vibration assembly having a reinforcement member of a single ring structure, in accordance with some embodiments of the present disclosure; FIG. [Figure 17] FIG. 2 is a partial schematic diagram of a vibration assembly according to some embodiments of the present disclosure. [Figure 18] FIG. 13 is a schematic diagram of deformation at a third resonant peak of a vibration assembly according to some further embodiments of the present disclosure. [Figure 19] FIG. 13 is a schematic diagram illustrating deformation at a third resonance peak of a vibration assembly according to some further embodiments of the present disclosure. [Figure 20] FIG. 20 is a frequency response curve diagram of the vibration assembly shown in FIG. 19. [Figure 21] FIG. 13 is another frequency response curve diagram of a vibration assembly in accordance with certain embodiments of the present disclosure. [Figure 22A]FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 22B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 23A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 23B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 23C] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 23D] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 24A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 24B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 25A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 25B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 25C] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 25D] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 25E] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 26A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 26B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 27A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 27B]FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 27C] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 28] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 29] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 30A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 30B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 30C] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 30D] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 30E] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Diagram 31] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Diagram 32] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 33A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 33B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 34A] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 34B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 34C] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 35A]FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 35B] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 35C] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. [Figure 35D] FIG. 2 is a schematic diagram of a vibration assembly according to some further embodiments of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0043] In order to more clearly describe the technical means of the embodiments of the present specification, the drawings necessary for the description of the embodiments will be briefly described below. Obviously, the drawings described below are only some of the examples or embodiments of the present specification, and those skilled in the art can apply the present specification to other similar scenarios based on these drawings without creative efforts. Unless otherwise clear from the context or described otherwise, the same symbols in the drawings represent the same structures or operations.

[0044] It should be understood that the terms "system," "apparatus," "unit," and / or "module" used herein are ways of distinguishing between different levels of assemblies, elements, components, parts, or structures, however, other terms may be used in place of the above terms if they achieve the same purpose.

[0045] As used in this specification and claims, unless the context clearly dictates otherwise, terms such as "a," "one," "one kind," and / or "the" do not specifically refer to the singular but may include the plural. In general, the terms "comprise" and "containing" are merely intended to indicate the inclusion of explicitly identified steps and elements, and these steps and elements are not intended to be an exclusive listing, and a method or apparatus may include other steps or elements.

[0046] Flowcharts are used herein to describe operations performed by the system according to the embodiments of the present invention. It should be understood that the preceding and subsequent operations are not necessarily performed in exact order. Instead, the steps may be processed in reverse order or simultaneously. Also, other operations may be added to these processes, or one or more operations may be removed from these processes.

[0047] The embodiments of the present specification provide a vibration assembly applicable to various sound output devices. The sound output devices include, but are not limited to, speakers, hearing aids, etc. The vibration assembly according to the embodiments of the present specification mainly includes an elastic element, which may be connected to a driving part of a speaker, and an edge of the elastic element is fixed (e.g., connected to a housing of the speaker). In the speaker, the driving part of the speaker, as an electric energy-mechanical energy conversion unit, provides a driving force to the speaker by converting electric energy into mechanical energy. The vibration assembly can generate sound pressure by pushing and moving air by receiving a force or displacement transmitted from the driving part and generating a corresponding vibration output. The elastic element can be considered to be connected to an air inertial load part by a spring and damping, and to realize the radiation of sound pressure by pushing and moving air.

[0048] The elastic element mainly includes a central region, an edge region disposed on the periphery of the central region, and a fixed region disposed on the periphery of the edge region. In some embodiments, in order to make the speaker have a flat sound pressure level output in a wide range (e.g., 20Hz to 20kHz), a given pattern is designed on the edge region of the elastic element to destroy the vibration mode in the corresponding frequency band of the edge region of the elastic element, and the cancellation of the sound caused by the local split vibration of the elastic element is avoided, and the local stiffness of the elastic element is improved by designing the pattern. Furthermore, by designing a thick structure on the central region of the elastic element, the stiffness of the central region of the elastic element is improved, and the cancellation of the sound caused by the split vibration mode in the range of 20Hz to 20kHz of the central region of the elastic element of the speaker is avoided. However, directly designing a thick layer on the central region of the elastic element increases the mass of the entire vibration assembly, increases the load on the speaker, and causes impedance mismatch between the driving end and the load end, resulting in a decrease in the sound pressure level output from the speaker. In the vibration assembly according to the embodiment of the present specification, the central region of the elastic element is designed so that the central region of the elastic element includes an elastic member and a reinforcing member stacked along the vibration direction, and the reinforcing member has a plurality of groove structures with openings facing the elastic member. In the vibration assembly according to the embodiment of the present specification, the central region of the elastic element is also designed so that the central region includes a reinforcing region and an elastic region arranged in parallel, and the reinforcing region has a plurality of groove structures with openings facing the vibration direction. The reinforcing region may correspond to a projection region of the reinforcing member onto the elastic member along the vibration direction. By designing the reinforcing member / reinforcing region with a groove structure, the vibration assembly has a required high-order mode at mid-high frequencies (3 kHz or more), and by designing the arrangement and dimensions of the reinforcing member / reinforcing region with a groove structure, three or less resonance peaks appear in an appropriate frequency band of the frequency response curve of the vibration assembly, and the vibration assembly has high sensitivity in a wide frequency band range, and by providing the reinforcing member / reinforcing region with a groove structure, the vibration assembly has a small mass, a large rigidity, and an improved sensitivity of the entire speaker. For specific details regarding the vibration assembly, the elastic element, and the reinforcing member / reinforcing region, please refer to the following related description.

[0049] Please refer to FIG. 1, which is a schematic diagram of a vibrating assembly and its equivalent vibration model, according to some embodiments herein.

[0050] In some embodiments, the vibrating assembly 100 mainly includes an elastic element 110, which includes a central region 112, an edge region 114 disposed on the outer periphery of the central region 112, and a fixing region 116 disposed on the outer periphery of the edge region 114. The elastic element 110 is configured to vibrate along a direction perpendicular to the central region 112, and transmits the force and displacement received by the vibrating assembly 100 to push and move air. The central region 112 includes an elastic member and a reinforcing member 120 laminated along the vibration direction. The vibration direction is the vibration direction of the elastic element 110, i.e., a direction perpendicular to the central region 112, and in FIG. 1, the vibration direction is a direction perpendicular to the paper plane of FIG. 1. In some embodiments, the elastic member may be a portion located in the central region of the elastic element 110. The reinforcing member 120 is connected to the elastic member and includes a groove structure 121 (shown in FIG. 7A), and the groove structure 121 has an opening toward the elastic member. In some embodiments, the reinforcing member 120 includes one or more annular structures 122 and one or more elongated structures 124, each of which is connected to at least one of the one or more annular structures 122. A groove structure 121 is provided on a cross section of the elongated structures 124 and / or the annular structures 122. By rationally providing the reinforcing member 120, the local stiffness of the central region 112 of the elastic element 110 can be controlled to avoid a state of sound cancellation due to split vibration modes in a wide range (e.g., 20 Hz to 20 kHz) of the central region 112 of the elastic element 110 of the vibration assembly 100, and the vibration assembly 100 has a flat sound pressure level curve. By arranging one or more elongated structures 124 and one or more annular structures 122 so that they are connected to each other and surround the openwork structure, the reinforcing member 120 has an appropriate ratio of groove structure (i.e., elongated structure 124 or annular structure 122) and openwork structure (i.e., openwork portion), the mass of the reinforcing member 120 is reduced, and the sensitivity of the entire vibration assembly 100 is improved. Furthermore, by designing the shape, dimensions and number of the elongated structures 124 and / or annular structures 122 and groove structures 121, the positions of multiple resonant peaks of the vibration assembly 100 can be adjusted to control the vibration output of the vibration assembly 100.

[0051] In some embodiments, the central region 112 includes a juxtaposed reinforcing region and an elastic region (see FIG. 7F ), where the reinforcing region and the elastic region may be a reinforcing member 120 and an elastic member, respectively. In this case, the elastic member is connected to a side of the structure of the reinforcing member 120 (e.g., a skirt structure of the groove structure 121). The reinforcing member 120 includes one or more annular structures 122 and one or more elongated structures 124, where each of the one or more elongated structures 124 is connected to at least one of the one or more annular structures 122. The groove structure 121 is disposed on a transverse surface of the elongated structure 124 and / or the annular structure 122, and the groove structure 121 is formed with an opening toward the vibration direction.

[0052] The elastic element 110 may be an element that can be elastically deformed by an external load. In some embodiments, the elastic element 110 may be a heat-resistant material so as to maintain performance in a processing and manufacturing process when the vibration assembly 100 is applied to a vibration sensor or speaker. In some embodiments, the Young's modulus and shear modulus of elasticity of the elastic element 110 do not change or change slightly (e.g., within 5%) when the elastic element 110 is in an environment of 200°C to 300°C, and the Young's modulus may represent the deformation ability of the elastic element 110 when it is pulled or compressed, and the shear modulus may represent the deformation ability of the elastic element 110 when it is sheared. In some embodiments, the elastic element 110 may be a material having excellent elasticity (i.e., easily elastically deformed) so that the vibration assembly 100 has excellent vibration response. In some embodiments, the material of the elastic element 110 may be one or more of organic polymer materials, rubber-based materials, and the like.In some embodiments, the organic polymeric material may be polycarbonate (PC), polyamides (PA), acrylonitrile butadiene styrene (ABS), polystyrene (PS), high impact polystyrene (HIPS), polypropylene (PP), polyethylene terephthalate (PET), polyvinyl chloride (PVC), polyurethanes (PU), polyethylene (PE), phenolic resins (Phenol), polystyrene (PS), polyvinyl chloride (PVC), urethanes (PU), polyethylene (PE), phenolic resins (Phenol), polystyrene (PS), polyvinyl chloride (PVC), urethanes (PU), polyethylene (PE), phenolic resins (Phenol), polystyrene (PS), polyvinyl chloride (PVC), urethanes (PU), polyethylene (PE), phenolic resins (Phenol), polystyrene (PS), polyvinyl chloride (PVC), urethanes (PU), polyethylene (PE), phenolic resins (Phenol), polystyrene (PS), polystyrene (PS), polyvinyl chloride (PVC), urethanes (PU), polystyrene (PE), phenolic resins (Phenol), polystyrene (PS ... Formaldehyde (PF), urea-formaldehyde resin (UF), melamine-formaldehyde resin (MF), polyarylate (PAR), polyetherimide (PEI), polyimide (PI), polyethylene naphthalate (PEN), polyetheretherketone (PEEK), carbon fiber, graphene, silica gel, etc., or a combination thereof. In some embodiments, the organic polymer material may be various rubber-based materials, including, but not limited to, gel-based, silicone gel, acrylic acid-based, polyurethane-based, rubber-based, epoxy-based, hot melt-based, photocuring-based, etc., and may be preferably a silicone adhesive adhesive or a silicone sealant adhesive.

[0053] The Shore hardness of the elastic element 110 may represent resistance to local deformation. The higher the Shore hardness, the stronger the resistance to local deformation (especially plastic deformation), and the less likely local deformation occurs. In some embodiments, the Shore hardness of the elastic element 110 may be 1HA to 50HA in order to vibrate the elastic element 110 with an appropriate drive. In some embodiments, the Shore hardness of the elastic element 110 may be 1HA to 15HA in order to reduce the difficulty of vibrating the elastic element 110. In some embodiments, the Shore hardness of the elastic element 110 may be 14.9HA to 15.1HA in order to provide resistance to plastic deformation of the elastic element 110. The Shore hardness of the elastic element 110 may be measured by a Shore hardness tester. Specifically, a sample of the elastic element 110 is placed on a hard platform, and an appropriate force is applied to a zero-reset Shore hardness tester so that its needle is pressed vertically against the sample surface at a constant speed until the needle end face of the Shore hardness tester completely contacts the sample surface, at which point the measured value on the dial of the Shore hardness tester is recorded, which is the Shore hardness of the elastic element 110. In some embodiments, when the thickness of the elastic element 110 is thin, samples of the same specification and the same lot can be stacked to a certain thickness (e.g., 3 mm or more) for measurement.

[0054] The Young's modulus of the elastic element 110 may represent the ability of the elastic element 110 to elastically deform when subjected to a force. The higher the Young's modulus, the stronger the resistance to deformation of the material, the higher the stiffness, and the less likely it is to deform. In some embodiments, in order to vibrate the elastic element 110 with an appropriate drive, the Young's modulus of the elastic element 110 is in the range of 5E8 Pa to 1E10 Pa. In some embodiments, in order to appropriately provide the elastic deformation capability of the elastic element 110, the Young's modulus of the elastic element 110 is in the range of 1E9 Pa to 5E9 Pa. In some embodiments, in order to appropriately provide the elastic deformation capability of the elastic element 110, the Young's modulus of the elastic element 110 is in the range of 1E9 Pa to 4E9 Pa. In some embodiments, in order to appropriately provide the elastic deformation capability of the elastic element 110, the Young's modulus of the elastic element 110 is in the range of 2E9 Pa to 5E9 Pa. In some embodiments, the method for measuring the Young's modulus of the elastic element 110 may include various methods, such as a resonance method, a nanoindentation method, a dynamic expansion method, a visual image tracking system, and a micro-stretching composite method. For example, the elastic element 110 is a thin film material that can excite a surface acoustic wave on the surface of the thin film by a laser pulse, and the velocity dispersion relationship of the surface acoustic wave is determined by the elastic modulus (Young's modulus), density, and thickness of the thin film and the substrate, so that the Young's modulus, density, and thickness of the thin film can be measured by detecting the velocity of the surface acoustic wave based on the fact that the propagation speed of the surface acoustic wave differs in different materials. Specifically, by comparing the velocity dispersion relationship of the sound wave detected by the acoustic detector with the dispersion relationship calculated by a theoretical model, information such as the Young's modulus, density, and thickness of the thin film can be obtained.

[0055] In some embodiments, for a given volume of the elastic element 110, in order to approximate the mass of the elastic element 110, the density of the elastic element 110 is 1E3 kg / m 3 ~4E3kg / m 3 In some embodiments, to accommodate the mass of the elastic element 110, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~2E3kg / m 3 In some embodiments, to accommodate the mass of the elastic element 110, the density of the elastic element 110 is in the range of 1E3 kg / m3 ~3E3kg / m 3 In some embodiments, to avoid the mass of the elastic element 110 being too large, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~1.5E3kg / m 3 In some embodiments, to avoid the mass of the elastic element 110 being too small, the density of the elastic element 110 is in the range of 1.5E3 kg / m 3 ~2E3kg / m 3 is in the range.

[0056] The central region 112 is a region of the elastic element 110 that extends from the center (e.g., the center of gravity) to the periphery by a certain area. The central region 112 includes an elastic member and a reinforcing member 120, and the reinforcing member 120 is connected to the elastic member. In some embodiments, the elastic member may be a portion located in the central region 112 of the elastic element 110, and the elastic member and the reinforcing member 120 are stacked and installed along the vibration direction, and the surface of the elastic member close to the reinforcing member 120 is connected to the side where the opening of the groove structure 121 of the reinforcing member 120 is installed. In this case, the surface of the elastic member can completely cover the reinforcing member 120, that is, the elastic member can cover the opening of the groove structure 121 of the reinforcing member 120. In some other embodiments, the elastic member (i.e., the elastic region of the central region) and the reinforcing member 120 (i.e., the reinforcing region of the central region) are arranged in parallel, and the elastic member is connected to the side of the openwork structure of the reinforcing member 120. In this case, the elastic member can cover the portion of the central region 112 that is not covered by the reinforcing member 120, i.e., the elastic member can not cover or only partially cover the opening of the groove structure 121 of the reinforcing member 120.

[0057] In some embodiments, when the vibration assembly 100 is applied to a speaker, the elastic member in the central region 112 may be directly connected to a driving part of the speaker. In other embodiments, the reinforcing member 120 in the central region 112 may be directly connected to a driving part of the speaker. The elastic element 110 is configured to vibrate along a direction perpendicular to the central region 112, and the elastic member in the central region 112 and the reinforcing member 120 can transmit the force and displacement of the driving part to push and move air and output sound pressure.

[0058] The edge region 114 is located outside the central region 112. In some embodiments, the edge region 114 may be designed with a unique pattern to destroy the vibration mode of the elastic element 110 in the corresponding frequency band of the edge region 114, avoid sound cancellation caused by localized division vibration of the elastic element 110, and improve the local stiffness of the elastic element 110 through the pattern design.

[0059] In some embodiments, the edge region 114 may include an edge structure. In some embodiments, by adjusting parameters such as an edge width and an arch height of the edge structure, the stiffness of the edge region 114 corresponding to the edge structure is different, and the frequency band of the corresponding high-frequency localized split vibration mode is also different. The edge width may be a radial width of the projection of the edge region 114 along the vibration direction of the elastic element 110. The arch height is a height that protrudes from the center region 112 or the fixed region 116 along the vibration direction of the elastic element 110 of the edge region 114.

[0060] In some embodiments, the maximum area of ​​the projection of the outermost annular structure 122 of the reinforcing member 120 along the vibration direction of the elastic element 110 is smaller than the area of ​​the central region 112. That is, between the outermost projection of the reinforcing member 120 and the edge region 114, there is an area that is not supported by the reinforcing member 120, and a part of the central region 112 between the edge region 114 and the reinforcing member 120 is referred to as a suspension region 1121 in this specification. The part of the elastic element 110 corresponding to the suspension region 1121 is also referred to as an elastic member. In some embodiments, the area of ​​the suspension region 1121 can be adjusted by adjusting the maximum contour of the reinforcing member 120 to adjust the mode vibration mode of the vibrating assembly.

[0061] The fixing region 116 is disposed on the outer periphery of the edge region 114. The elastic element 110 can be connected and fixed via the fixing region 116. For example, the elastic element 110 can be connected and fixed to a speaker housing or the like via the fixing region 116. In some embodiments, the fixing region 116 can be considered to be attached and fixed to the speaker housing and not involved in the vibration of the elastic element 110. In some embodiments, the fixing region 116 of the elastic element 110 can be connected to the speaker housing via a support element. In some embodiments, the support element can include a soft material that is easily deformed so as to deform and provide a larger displacement to the vibration of the vibration assembly 100 when the vibration assembly 100 vibrates. In other embodiments, the support element can include a hard material that is not easily deformed.

[0062] In some embodiments, the elastic element 110 may further include a connection region 115 disposed between the edge region 114 and the anchoring region 116. In some embodiments, the connection region 115 can tune the modal vibration modes of the vibrating assembly 100 by providing additional stiffness and damping to the vibration of the elastic element 110.

[0063] In order for the elastic element 110 to provide an appropriate stiffness, the thickness and elastic modulus of the elastic element 110 can be set in a reasonable range. In some embodiments, the thickness of the elastic element 110 may be in a range of 3 μm to 200 μm. In some embodiments, in order to avoid the elastic element 110 having too high a stiffness, the thickness of the elastic element 110 may be in a range of 3 μm to 100 μm. In some embodiments, in order to avoid the elastic element 110 having too high a stiffness, the thickness of the elastic element 110 may be in a range of 3 μm to 50 μm.

[0064] The reinforcing member 120 may be an element for increasing the stiffness of the elastic element 110. In some embodiments, the reinforcing member 120 is connected to the central region 112, and the reinforcing member 120 and / or the central region 112 are connected to a driver of a speaker to transmit force and / or displacement so that the vibrating assembly 100 pushes and displaces air to output sound pressure.

[0065] In some embodiments, the reinforcing member 120 may include one or more annular structures 122 and one or more elongated structures 124, each of which is connected to at least one of the one or more annular structures 122 to provide cross support to the central region 112 of the elastic element 110. At least one of the one or more elongated structures 124 extends toward the center of the central region 112. In some embodiments, the one or more elongated structures 124 may pass through the center of the central region 112 to support the center of the central region 112. In some embodiments, the reinforcing member 120 may further include a central connection 123, in which the one or more elongated structures 124 cover the center of the central region 112 without passing through the center of the central region 112, and the one or more elongated structures 124 may be connected to the central connection 123.

[0066] In some embodiments, a groove structure 121 may be provided on the cross-section of one or more annular structures 122 and / or one or more elongated structures 124. The provision of the groove structure 121 can adjust the stiffness and mass of the reinforcing member 120, avoid excessive increase in the load on the speaker, avoid impedance mismatch between the driving part and the load part, and improve the output effect of the vibration assembly 100.

[0067] The annular structure 122 may be a structure that extends around a specific center. In some embodiments, the center surrounded by the annular structure 122 may be the center of the central region 112. In some other embodiments, the center surrounded by the annular structure 122 may be another location that is offset from the center of the central region 112. In some embodiments, the annular structure 122 may be a structure with a closed contour. In some embodiments, the shape of the projection of the annular structure 122 along the vibration direction of the elastic element 110 may include, but is not limited to, one or more combinations of a circular ring, a polygonal ring, a curved ring, or an elliptical ring. In some other embodiments, the annular structure 122 may be a structure with an open contour. For example, the annular structure 122 may be a circular ring, a polygonal ring, a curved ring, or an elliptical ring having a notch. In some embodiments, the number of the annular structures 122 may be one. In some embodiments, the number of the annular structures 122 may be more than one, and the multiple annular structures may have the same center of gravity. In some embodiments, the number of the annular structures 122 may be in the range of 1 to 10. In some embodiments, the number of the annular structures 122 may range from 1 to 5. In some embodiments, the number of the annular structures 122 may range from 1 to 3. If the number of the annular structures 122 is too large, the mass of the reinforcing member 120 may be too large, which may further cause the sensitivity of the entire vibration assembly 100 to be reduced. In some embodiments, the number of the annular structures 122 may be designed to adjust the mass and stiffness of the reinforcing member 120. In some embodiments, the size of the annular structure 122 located at the outermost periphery of the reinforcing member 120 may be considered as the maximum size of the reinforcing member 120. In some embodiments, by setting the size of the annular structure 122 located at the outermost periphery, the size (or area) of the suspension region 1121 between the edge region 114 and the reinforcing member 120 may be adjusted to change the mode vibration mode of the vibration assembly 100.

[0068] In some embodiments, the one or more annular structures 122 may include a first annular structure and a second annular structure, where the radial dimension of the first annular structure is smaller than the radial dimension of the second annular structure. In some embodiments, the first annular structure is disposed inside the second annular structure. In some embodiments, the first annular structure and the second annular structure may have overlapping centers of gravity. In other embodiments, the first annular structure and the second annular structure may not have overlapping centers of gravity. In some embodiments, the first annular structure and the second annular structure may be connected via one or more elongated structures 124.

[0069] The elongated structure 124 may have any extension rule. In some embodiments, the elongated structure 124 may extend along a straight line. In some embodiments, the elongated structure 124 may extend along a curved line. In some embodiments, extending along a curved line may include, but is not limited to, extending in an arc, extending in a spiral, extending in a spline curve, extending in an arc, and extending in an S-shape. In some embodiments, the elongated structure 124 is connected to the annular structure 122 to divide the annular structure 122 into a plurality of openwork structures. That is, the openwork structure is provided in the reinforcing member 120 in an area other than the groove structure 121. In some embodiments, the area corresponding to the openwork structure of the central region 112 may be referred to as an openwork area (i.e., an elastic area). In some embodiments, the number of the elongated structure 124 may be one. For example, one elongated structure 124 may be located along any diameter of the annular structure 122, and the elongated structure 124 is connected to both the center of the central region (i.e., the center of gravity of the annular structure 122) and the annular structure 122. In some embodiments, the number of elongated structures 124 may be multiple. In some embodiments, multiple elongated structures 124 may be located along multiple diameters of the annular structure 122. In some embodiments, the multiple elongated structures 124 may extend toward a central location of the central region 112, which may be the center of gravity of the elastic element 110. In some embodiments, the multiple elongated structures 124 may be connected to a central location of the central region and form a central connection 123 at the central location. In some embodiments, the central connection 123 may be a separate structure, and multiple elongated structures 124 may be connected to the central connection 123. In some embodiments, the shape of the central connection 123 may include, but is not limited to, a circle, a square, a polygon, an ellipse, or the like. In some embodiments, the shape of the central connection portion 123 may be arbitrarily set.

[0070] In some embodiments, the number of elongated structures 124 may range from 1 to 100 to improve the stiffness of the elastic element 110. In some embodiments, the number of elongated structures 124 may range from 1 to 50 to avoid the stiffness of the elastic element 110 being too high. In some embodiments, the number of elongated structures 124 may range from 1 to 40 to avoid the stiffness of the elastic element 110 being too high. In some embodiments, the number of elongated structures 124 may range from 1 to 30 to avoid the stiffness of the elastic element 110 being too high. By setting the number of elongated structures 124, the mass of the entire vibrating assembly 100, the stiffness of the reinforcing member 120, and the area of ​​the openwork region of the elastic element 110 can be adjusted to change the modal vibration mode of the vibrating assembly.

[0071] In some embodiments, the shape of the projection of the elongated structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape. By designing different shapes of the elongated structure 124, the mass distribution (e.g., the location of the center of mass) of the stiffening member 120, the stiffness of the stiffening member 120, and the area of ​​the openwork region can be adjusted to change the modal vibration modes of the vibrating assembly.

[0072] It should be noted that in the embodiment of the present specification, the structures described for the annular structure 122 and the elongated structure 124 are merely preferred structures selected to rationally install the structure of the reinforcing member 120, and should not be understood as limiting the shape of the reinforcing member 120 and each part thereof. In fact, in the reinforcing member 120 in the embodiment of the present specification, the annular structure 122 and the elongated structure 124 having the groove structure 121 can form an openwork structure (corresponding to the openwork area located in the central region 112) between the annular structure 122 and the elongated structure 124, and the parameters of the groove structure and the openwork structure (e.g., area, thickness of the groove structure, etc.) can be adjusted to realize the adjustment of the vibration characteristics (e.g., number and frequency range of resonance peaks) of the vibration assembly 100. In other words, for any shape of reinforcing member having a groove structure and an openwork structure, the purpose of adjusting the vibration performance of the vibration assembly (e.g., the number and position of resonant peaks, the shape of the frequency response curve, etc.) can be achieved by using the parameter setting method of the groove structure and openwork structure provided in this specification, and all of these means should be included in the scope of this application.

[0073] In some embodiments, as shown in FIG. 1, the connection region 115 between the anchoring region 116 and the edge region 114 of the elastic element 110 is mounted in a suspended manner and has an equivalent mass of Mm 1 and the region is fixedly connected to the housing via a spring Km and a damping Rm, and the connection region 115 is fixedly connected to the housing via a spring Ka 1 , attenuation Ra 1 1. The elastic element 110 is connected to the air load at the front end thereof via a spring 116 to transmit force and displacement to push and move the air.

[0074] In some embodiments, the edge region 114 of the elastic element 110 has a local equivalent mass Mm 2 and the region has a spring Ka' 1 , attenuation Ra' 1 and the edge region 114 is connected to the connection region 115 of the elastic element 110 via the spring Ka 2 , attenuation Ra 21. The elastic element 110 is connected to the air load at the front end thereof via a spring 116 to transmit force and displacement to push and move the air.

[0075] In some embodiments, a reinforcing member 120 is provided in the central region 112 of the elastic element 110, and the reinforcing member 120 is connected to the elastic member located in the central region 112, and there is a part of a suspension region 1121 between the region of the elastic member supported by the reinforcing member 120 and the edge region 114. The region has a local equivalent mass Mm 3 and the region has a spring Ka' 2 , attenuation Ra' 2 The edge region 114 is connected to the reinforcing member 120 via the spring Ka 3 , attenuation Ra 3 1. The elastic element 110 is connected to the air load at the front end thereof via a spring 116 to transmit force and displacement to push and move the air.

[0076] In some embodiments, depending on the design of the stiffening member 120, the central region 112 of the elastic element 110 corresponding to the stiffening member 120 may have one or more openwork regions, each of which may correspond to a mass-spring-damping system, with an equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i The openwork area has a spring Ka' i , attenuation Ra' i The openwork area is further connected to the adjacent openwork area via a spring Ka' i , attenuation Ra' i 11, the central region 112 is connected to a suspension region 1121 between the region supported by the reinforcing member 120 and the edge region 114 via a spring Ka i , attenuation Ra i 1. The elastic element 110 is connected to the air load at the front end thereof via a spring 116 to transmit force and displacement to push and move the air.

[0077] In some embodiments, the stiffening member 120 itself has an equivalent mass Mm nThe reinforcing member 120 has a spring Ka' n , attenuation Ra' n The reinforcing member 120 is connected to the central region 112 via a spring Ka n , attenuation Ra n When the reinforcing member 120 itself resonates, it drives the central region 112 and the elastic element 110 to generate large travel speeds and displacements, thereby generating high sound pressure levels.

[0078] Based on the dynamic characteristics of the mass-spring-damping system, each mass-spring-damping system has its own resonant peak frequency f0 and can generate large moving speeds and displacements at f0; by designing different parameters of the vibration assembly 100 (e.g., the structural parameters of the elastic element 110 and / or the reinforcing member 120), the mass-spring-damping systems formed by the structures at different positions of the vibration assembly 100 can resonate in the required frequency band; furthermore, the frequency response curve of the vibration assembly 100 has multiple resonant peaks, thereby greatly widening the effective frequency band of the vibration assembly 100; and by designing the reinforcing member 120, the vibration assembly 100 can have a lighter mass and output a higher sound pressure level.

[0079] FIG. 2 is a diagram of deformation at a first resonant peak of a vibration assembly according to some embodiments of the present specification, FIG. 3 is a diagram of deformation at a second resonant peak of a vibration assembly according to some embodiments of the present specification, and FIG. 4 is a diagram of deformation at a third resonant peak of a vibration assembly according to some embodiments of the present specification.

[0080] As can be seen from the schematic diagram of the equivalent vibration model of the vibration assembly 100 shown in FIG. 1, each part of the vibration assembly 100 resonates at different frequency bands, and by outputting large velocity values ​​in the corresponding frequency bands, large sound pressure values ​​are output in the corresponding frequency bands of the frequency response curve of the vibration assembly 100, and corresponding resonance peaks appear, and due to the multiple resonance peaks, the frequency response of the vibration assembly 100 has high sensitivity within the audible sound range (e.g., 20 Hz to 20 kHz).

[0081] As shown in FIGS. 1 and 2, in some embodiments, the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent mass of the driving end are combined to form a total equivalent mass Mt, and the equivalent damping of each part forms a total equivalent damping Rt, and the elastic element 110 (especially the edge region 114, and the elastic element 110 in the suspension region between the edge region 114 and the stiffening member 120) has a large compliance and provides a stiffness Kt to the system, forming a mass Mt-spring Kt-damping Rt system, which has a resonant frequency, and when the excitation frequency of the driving end is close to the velocity resonant frequency of the system, the system resonates (as shown in FIG. 2) and has a large velocity value v in a frequency band near the velocity resonant frequency of the Mt-Kt-Rt system. a The sound pressure amplitude and the sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this specification defines this resonance peak as the first resonance peak of the vibration assembly 100. In some embodiments, as shown in FIG. 2, FIG. 2 shows the vibration situation of the vibration assembly 100 in the AA cross section, where the white structure in FIG. 2 represents the shape and position of the reinforcing member 120 before deformation, and the black structure represents the shape and position of the reinforcing member 120 at the first resonance peak. Note that FIG. 2 shows only the structure situation of the vibration assembly 100 from the center of the reinforcing member 120 to one side edge of the elastic element 110 in the AA cross section, that is, only half of the AA cross section, and the other half of the AA cross section that is not shown is symmetrical to the situation shown in FIG. 2. As can be seen from the vibration situation of the vibration assembly 100 in the AA cross section, at the position of the first resonance peak, the main deformation position of the vibration assembly 100 is the part connected to the fixed region 116 of the elastic element 110. In some embodiments, the frequency of the first resonant peak of the vibration assembly 100 (also referred to as the first resonant frequency) may be related to the ratio of the mass of the vibration assembly 100 to the elastic coefficient of the elastic element 110. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 2500 Hz in order to improve the sound pressure level output by the speaker in a wide mid-low frequency range (e.g., 20 Hz to 3500 Hz). In some embodiments, the frequency range of the first resonant peak is 400 Hz to 1500 Hz in order to mainly improve the sound pressure level output by the speaker in a general mid-low frequency range (e.g., 80 Hz to 2500 Hz). Preferably, the frequency range of the first resonant peak is 500 Hz to 1200 Hz. More preferably, the frequency range of the first resonant peak is 600 Hz to 1000 Hz. In some embodiments, the first resonant peak of the vibration assembly 100 can be set in the above frequency range by setting the structure of the reinforcing member 120.

[0082] As shown in FIGS. 1 and 3, the reinforcing member 120 itself has an equivalent mass Mm n The reinforcing member 120 has a spring Ka' n , attenuation Ra' n The reinforcing member 120 is connected to the central region 112 via a spring Kan , attenuation Ra n When the reinforcing member 120 itself resonates, it drives the central region 112 to drive the elastic element 110 to generate large movement velocities and displacements, thereby generating high sound pressure levels.

[0083] The reinforcing member 120, the connection region 115, the edge region 114, the suspension region 1121 between the region in the center region 112 where the reinforcing member 120 is installed and the edge region 114, the equivalent air mass, and the driving end equivalent mass are combined to form a total equivalent mass Mt 1 The equivalent damping of each part forms the total equivalent damping Rt 1 The reinforcing member 120 and the elastic element 110 (especially the area of ​​the central region 112 covered by the reinforcing member 120) have a high stiffness, providing the system with a stiffness Kt 1 To provide mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 The system has a vibration mode that forms a reverse motion by moving in opposite directions inside and outside the annular region, with an annular region in the diameter direction of the central region 112 as an equivalent fixed support, and the connection region 115, the edge region 114, and the suspension region 1121 between the region of the central region 112 where the reinforcing member 120 is installed and the edge region 114 are driven by the reinforcing member 120 to vibrate, realizing a resonance mode (shown in FIG. 3) with a reverse motion as a vibration mode, and the resonance also occurs when the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 When the excitation frequency of the driving end is close to the speed resonance frequency of the system, Mt 1 -Kt 1 -Rt 1 The system resonates and the Mt 1 -Kt 1 -Rt 1 Large speed values ​​v in the frequency band near the speed resonance frequency of the system a The sound pressure amplitude and the sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this resonance peak is defined as the second resonance peak of the vibration assembly 100 in this specification. In some embodiments, as shown in FIG. 3, FIG. 3 shows the vibration situation of the vibration assembly 100 in the AA cross section, where the white structure in FIG. 3 represents the shape and position of the reinforcing member 120 before deformation, and the black structure represents the shape and position of the reinforcing member 120 at the second resonance peak. Note that FIG. 3 shows only the structure situation of the vibration assembly 100 from the center of the reinforcing member 120 to one side edge of the elastic element 110 in the AA cross section, that is, only half of the AA cross section, and the other half of the AA cross section that is not shown is symmetrical to the situation shown in FIG. 3. As can be seen from the vibration situation of the vibration assembly 100 in the AA cross section, the main deformation position of the vibration assembly 100 around the frequency of the second resonance peak (also called the second resonance frequency) is the site of reverse deformation of the reinforcing member 120. In some embodiments, the second resonance peak of the vibration assembly 100 may be related to the stiffness of the reinforcing member 120. In some embodiments, the frequency range of the second resonance peak may be 5000 Hz to 10000 Hz in order to improve the sound pressure level output by the speaker in a wide mid-high frequency range (e.g., 3500 Hz to 11000 Hz). In some embodiments, the frequency range of the second resonance peak may be 6000 Hz to 8000 Hz in order to mainly improve the sound pressure level output by the speaker in a general mid-high frequency range (e.g., 4000 Hz to 10000 Hz). Preferably, the frequency range of the second resonance peak is 6500 Hz to 7500 Hz. In some embodiments, the second resonance peak of the vibration assembly 100 can be in the above frequency range by setting the structure of the reinforcing member 120.

[0084] As shown in FIGS. 1 and 4, the reinforcing member 120 has one or more openwork regions corresponding to the central region 112, and each openwork region is a mass-spring-damping system having an equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' iThe openwork area has a spring Ka' i , attenuation Ra' i and connected to the adjacent openwork area via a spring Ka' i , attenuation Ra' i 1121 between the area supported by the reinforcing member 120 of the central area 112 and the edge area 114, and the openwork area is connected to the suspension area 1121 between the area supported by the reinforcing member 120 of the central area 112 and the edge area 114 via the spring Ka i , attenuation Ra i 1. The elastic element 110 is connected to the air load at the front end thereof via a spring 116 to transmit force and displacement to push and move the air.

[0085] Since the openwork areas are spaced apart by the elongated structures 124 and / or the annular structures 122 of the reinforcing member 120, each openwork area can form a different resonant frequency and independently push and move the air area connected thereto to generate a corresponding sound pressure; further, by designing the position, size, and number of each elongated structure 124 and / or the annular structures 122 of the reinforcing member 120, each openwork area can be realized to have a different resonant frequency, so that one or more high-frequency resonant peaks (i.e., the third resonant peak) appear in the frequency response curve of the vibration assembly 100. In some embodiments, the one or more high-frequency resonant peaks (i.e., the third resonant peak) may be in the range of 12000Hz to 18000Hz to improve the sound pressure level output by the speaker in a wide high-frequency range (e.g., 11000Hz to 20000Hz). In some embodiments, the frequency range of the third resonant peak may be 13000Hz to 17000Hz, in order to primarily improve the sound pressure level output by the speaker in a typical high frequency range (e.g., 12000Hz to 18000Hz). Preferably, the frequency range of the third resonant peak is 14000Hz to 16000Hz. More preferably, the frequency range of the third resonant peak is 14500Hz to 15500Hz.

[0086] Furthermore, in order to improve the sound pressure level output by the vibrating assembly 100 at high frequencies (10000Hz to 20000Hz), the resonant frequencies of the openwork regions are equal or close to each other by designing the position, size, and number of each elongated structure 124 and / or annular structure 122. In some embodiments, by making the resonant frequency difference between each openwork region in the range of 4000Hz, a high-frequency resonant peak with a high output sound pressure level appears on the frequency response curve of the vibrating assembly 100, and this resonant peak is defined herein as the third resonant peak of the vibrating assembly 100. In some embodiments, the frequency range of the third resonant peak may be 12000Hz to 18000Hz.

[0087] In some embodiments, the resonant frequency of each openwork region can be adjusted by designing the area of ​​one or more openwork regions and the thickness of the elastic element 110, so that the third resonant peak of the vibrating assembly 100 is in the above frequency range. That is, the frequency range of the third resonant peak can be adjusted by designing the range of the ratio between the area of ​​each openwork region and the thickness of the elastic element 110. The area of ​​each openwork region is in mm 2 The thickness of the elastic element 110 may be in mm, and the ratio of the area of ​​each openwork area to the thickness of the elastic element 110 may be in mm. Illustratively, when the area of ​​a certain openwork area is 20 mm 2and the thickness of the elastic element 110 is 0.2 mm, the ratio of the area of ​​the openwork area to the thickness of the elastic element 110 is 100 mm. In some embodiments, in order to set the third resonance peak of the vibrating assembly 100 in a frequency range of 12000 Hz to 18000 Hz, the ratio of the area of ​​each openwork area to the thickness of the elastic element 110 is in the range of 100 mm to 1000 mm. In some embodiments, in order to set the third resonance peak of the vibrating assembly 100 in a frequency range of 14000 Hz to 16000 Hz, the ratio of the area of ​​each openwork area to the thickness of the elastic element 110 is in the range of 120 mm to 900 mm. In some embodiments, in order to set the third resonance peak of the vibrating assembly 100 in a frequency range of 14500 Hz to 15500 Hz, the ratio of the area of ​​each openwork area to the thickness of the elastic element 110 is in the range of 150 mm to 800 mm. In some embodiments, in order to place the third resonant peak of the vibrating assembly 100 in the frequency range of 14700 Hz to 15200 Hz, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in the range of 150 mm to 700 mm.

[0088] As shown in FIG. 5A, FIG. 5A is a frequency response curve diagram of a vibration assembly according to some embodiments of the present specification. By designing the structure of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 can be realized to have multiple resonance peaks in the audible range, and further, the combination of multiple resonance peaks, etc., allows the vibration assembly 100 to have high sensitivity in the entire audible range. By designing the structure of the reinforcing member 120, the third resonance peak 240 of the vibration assembly 100 can be realized to be in a different frequency range. By designing the frequency difference between the third resonance peak 240 and the second resonance peak 230, the frequency response curve can be realized to be flat and the output sound pressure level can be high in the frequency band between the third resonance peak 240 and the second resonance peak 230, and the appearance of a valley in the frequency response curve can be avoided.

[0089] As shown in FIG. 5A, due to the design of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 has the required higher-order modes in the audible range (20 Hz to 20,000 Hz), and the above-mentioned first resonance peak 210, second resonance peak 230 and third resonance peak 240 appear on the frequency response curve of the vibration assembly 100, that is, the number of resonance peaks on the frequency response curve of the vibration assembly 100 in the frequency range of 20 Hz to 20,000 Hz is three, so that the vibration assembly 100 has high sensitivity in a wide frequency band range.

[0090] In some embodiments, by designing the structure of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 can have only two resonance peaks in the audible range (20Hz-20000Hz). For example, by designing the structure of the reinforcing member 120 (including the overall dimension of the reinforcing member 120, the number, dimensions, etc. of the elongated structures 124 and / or annular structures 122 having groove structures 121 in their cross sections), the size of each openwork area can be designed, thereby adjusting the resonance frequency of the corresponding suspension area 1121, so that the third resonance peak 240 formed by the vibration assembly 100 at high frequency is not obvious and does not appear in the frequency response curve. If the resonant frequency of each suspension area 1121 is made higher than the audible range, or the resonant frequencies of each suspension area 1121 are different and different suspension areas 1121 have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving the sound overlap cancellation effect, the effect of high frequency roll-off can be obtained, and the third resonant peak 240 does not appear in the sound pressure level frequency response curve of the vibrating assembly 100.

[0091] As shown in FIG. 5B, FIG. 5B is a frequency response curve diagram when the vibration assembly according to some embodiments of the present specification does not have a third resonance peak. By designing the annular structure 122 and the elongated structure 124 of the reinforcing member 120, the reinforcing member 120 has one or more openwork areas corresponding to the central region 112, and each openwork area becomes a mass-spring-damping system, and by designing the position, size, and number of each elongated structure 124 of the reinforcing member 120, the resonant frequency of each openwork area is equal or close. In some embodiments, the resonant frequency difference of each openwork area is in the range of 4000Hz, so that the frequency response curve of the vibration assembly 100 has one or more high frequency resonant peaks (i.e., third resonant peaks) with high output sound pressure levels.

[0092] In some embodiments, as shown in FIG. 5B, by designing the position, dimensions, and number of each elongated structure 124 and / or annular structure 122 of the reinforcing member 120, the resonant frequency of each openwork area is made higher than the audible sound range, or the resonant frequency of each openwork area is different and different openwork areas have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving the sound overlap cancellation effect, the effect of high frequency roll-off can be obtained, and the third resonant peak 240 does not appear in the sound pressure level frequency response curve of the vibrating assembly 100.

[0093] As shown in FIG. 6, FIG. 6 is a frequency response curve diagram of a vibration assembly including a groove structure and a vibration assembly not including a groove structure according to some embodiments of the present disclosure. In some embodiments, the mass and stiffness distribution of the stiffening member 120 can be effectively adjusted by designing the size and shape of the structure of the stiffening member 120 having the groove structure 121. In some embodiments, the stiffness Kt provided to the system by the stiffening member 120, the elastic element 110 (especially the central region 112 of the elastic element 110) can be adjusted by changing the stiffness of the stiffening member 120 itself while keeping or changing the mass of the stiffening member 120. 1 changes, and the mass Mt 1 -Spring Kt 1-Attenuation Rt 1 Changing the resonant frequency of the reversible motion of the system changes the position of the third resonant peak 240 of the vibrating assembly 100. In some embodiments, the output of the vibrating assembly 100 may be improved by reducing the mass of the stiffening member 120 without reducing the stiffness of the stiffening member 120.

[0094] As shown in Fig. 6, due to the design of the groove structure 121, the vibration assembly 100 has a flat frequency response output in the range of 1kHz to 6kHz, and the vibration assembly 100 forms a second resonance peak 230 and a third resonance peak 240 in the range of 6kHz to 10kHz and 12kHz to 18kHz, respectively, improving the sensitivity of the high frequency output. And, due to the design of the groove structure 121, the vibration assembly 100 has a highly sensitive output. Also, due to the design of the groove structure 121, the vibration assembly 100 has one or more resonance peaks at high frequencies, and the vibration assembly 100 has a highly sensitive output in a wide frequency band.

[0095] In some embodiments, by installing the groove structure 121, the rigidity of the reinforcing member 120 and the elastic element 110 can be ensured while reducing the mass of the reinforcing member 120, thereby improving the output of the vibration assembly 100 and having a positive impact on improving the performance of the vibration assembly 100.

[0096] 7A-7G are schematic diagrams of reinforcing members and elastic elements having different groove structures according to some embodiments herein. As shown in FIG. 7A-7E, in some embodiments, the reinforcing member 120 having the groove structure 121 and the elastic element 110 may be separate structures, and the two may form a hollow rigid reinforced structure after being assembled and molded. In some embodiments, the width of the groove structure 121 may be consistent in the vibration direction, for example, the groove structure 121 shown in FIG. 7A is a square U-shaped structure, and the groove structure 121 shown in FIG. 7B is a fillet U-shaped structure. In some embodiments, the width of the groove structure 121 may gradually decrease or increase in the vibration direction, for example, the groove structure 121 shown in FIG. 7C is a T-shaped structure, and the groove structure 121 shown in FIG. 7E is a cone-shaped protrusion structure. In some embodiments, the width of the groove structure 121 may be arbitrarily changed (for example, decreased and then increased), for example, the groove structure 121 shown in FIG. 7D is a U-shaped structure. By using a hollow structure, the groove structure 121 can be installed, which ensures the rigidity of the reinforcing member 120 and the elastic element 110 and reduces the mass of the reinforcing member 120, thereby improving the output of the vibration assembly 100.

[0097] As shown in FIG. 7F, in some embodiments, the reinforcing member 120 having the groove structure 121 and the elastic element 110 may be an integral structure, for example, both may be processed and molded at the same time. In some embodiments, when an integral structure is used, the groove structure 121 may be a U-shaped structure (for example, a square U-shaped structure shown in FIG. 7F) so as to facilitate design processing and reduce the difficulty of processing and manufacturing. In this case, the elastic member of the central region 112 of the elastic element 110 is placed between the groove structure 121 of the reinforcing member 120, and the elastic member is arranged as an elastic region in parallel with the reinforcing member 120 as a reinforcing region. In other embodiments, the groove structure 121 may be another type of hollow structure (for example, the above-mentioned U-shaped structure, T-shaped structure, etc.), as long as it is possible to ensure the rigidity of the reinforcing member 120 and the elastic element 110 and reduce the mass of the reinforcing member 120.

[0098] 7G, in some embodiments, a filling material may be installed in the hollow portion of the groove structure 121 of the reinforcing member 120 to adjust the mass and stiffness of the reinforcing member 120 and improve the output of the vibrating assembly 100. In some embodiments, the Young's modulus of the filling material may be smaller than the Young's modulus of the material of the elastic element 110 to reduce interference of the filling material with the vibration deformation of the elastic element 110. In some embodiments, the filling material may include a non-metallic material or a metallic material. In some embodiments, the non-metallic material of the filler material is selected from the group consisting of polycarbonate (PC), polyamides (PA), acrylonitrile butadiene styrene (ABS), polystyrene (PS), high impact polystyrene (HIPS), polypropylene (PP), polyethylene terephthalate (PET), polyvinyl chloride (PVC), polyurethanes (PU), polyethylene (PE), phenolic resins (Phenol), and the like. The filler material may include, but is not limited to, any one or combination of the following: polyetherimide (PEI), polyimide (PI), polyethylene naphthalate (PEN), polyetheretherketone (PEEK), carbon fiber, graphene, silica gel, etc. In some embodiments, the metal material of the filler material may include aluminum alloy, magnesium-lithium alloy, copper, stainless steel, etc.

[0099] As shown in FIG. 7A and FIG. 8, FIG. 8 is a schematic diagram of a groove structure according to some embodiments of the present specification. In some embodiments, the structure and dimensional parameters of the groove structure 121 have a large effect on the stiffness of the reinforcement member 120, so the stiffness and mass of the reinforcement member 120 can be adjusted by adjusting the structure and dimensional parameters of the groove structure 121. As shown in FIG. 8, the groove structure 121 has a height dimension h along the vibration direction and a width dimension w in a direction perpendicular to the vibration direction, the side wall of the groove structure 121 has a thickness dimension b, and a skirt structure perpendicular to the vibration direction (e.g., extending along the surface of the elastic member) is installed at the opening of the groove structure 121, and the width of the skirt structure is bm. The stiffness of the reinforcement member 120 having the groove structure 121 is mainly provided by the groove structure 121, and the stiffness of the groove structure 121, which is hollow inside, is mainly a bending stiffness EI, where E is Young's modulus and I is the moment of inertia. For the groove structures 121 shown in FIG. 7A and FIG. 8, the calculation formulas for the moment of inertia I of the corresponding reinforcing members 120 are as follows:

[0100] I=[wh^3-(w-2b){(h-2b)}^3 ] (Equation 1)

[0101] As can be seen from Equation 1, the moment of inertia I of the reinforcing member 120 having the groove structure 121 is determined only by the height h, width w and thickness b of the reinforcing member 120, where h and b are both cubed parameters, and their impact on the rigidity of the reinforcing member 120 having the groove structure 121 is particularly significant.

[0102] By designing the parameter h to increase, the inertia moment I increases, and the stiffness of the reinforcing member 120 having the groove structure 121 is further improved, so that the second resonance peak 230 of the speaker can move backward; conversely, by designing the parameter h to decrease, the stiffness of the reinforcing member 120 decreases, and the second resonance peak 230 of the vibration assembly 100 moves forward. Similarly, by designing the parameter b to increase, the inertia moment I increases, and the stiffness of the reinforcing member 120 having the groove structure 121 is further improved, so that the second resonance peak 230 of the vibration assembly 100 can move backward; conversely, by designing the parameter b to decrease, the stiffness of the reinforcing member 120 decreases, and the second resonance peak 230 of the vibration assembly 100 moves forward.

[0103] In some embodiments, the parameters h and b are optimized simultaneously, and the h value is optimized and increased while the b value is optimized and decreased, so that the stiffness of the reinforcing member 120 having the groove structure 121 does not change, the mass is reduced, the frequency value of the second resonant peak 230 of the vibrating assembly 100 does not change, and the output frequency response of the vibrating assembly 100 can be improved; conversely, the h value is optimized and decreased while the b value is optimized and increased, so that the stiffness of the reinforcing member 120 having the groove structure 121 does not change, the mass is increased, the frequency value of the second resonant peak 230 of the vibrating assembly 100 does not change, and the output frequency response of the vibrating assembly 100 can be reduced.

[0104] In some embodiments, by simultaneously optimizing the design of the parameters h and b, optimizing and increasing the h value and optimizing and decreasing the b value, the stiffness of the reinforcing member 120 having the groove structure 121 can be reduced, the mass can be reduced, the second resonant peak 230 of the vibration assembly 100 can be moved forward, and the output frequency response of the vibration assembly 100 can be improved.

[0105] In some embodiments, by simultaneously optimizing the design of the parameters h and b, and optimizing and increasing the h value and optimizing and decreasing the b value, the stiffness of the reinforcing member 120 having the groove structure 121 can be reduced, the mass can be increased, the second resonant peak 230 of the vibration assembly 100 can be moved forward, and the output frequency response of the speaker can be reduced.

[0106] The physical quantity λ is defined as the ratio of the height h to the thickness b of the reinforcing member 120 having the groove structure 121, that is, as follows:

[0107] λ=h / b (Equation 2)

[0108] As shown in FIG. 9, FIG. 9 is another frequency response curve diagram of the vibration assembly according to some embodiments of the present specification. As can be seen from FIG. 9, in some embodiments, by comparing the curve λ=5 with the curve λ=15, or λ=7.14, λ=9 and λ=12, by increasing the ratio λ, the effect of the frequency value of the second resonance peak 230 of the vibration assembly 100 not changing and the output increasing can be achieved. For example, the parameters h and b can be simultaneously optimized and designed, and the stiffness of the reinforcing member 120 having the groove structure 121 can be kept unchanged and the mass can be reduced by optimizing and increasing the h value and optimizing and decreasing the b value. In some embodiments, as can be seen from FIG. 9, with the increase of λ, the output of the vibration assembly 100 gradually increases. Specifically, when λ is small, for example, when λ=5, the output sound pressure level is obviously lower than when λ=12, λ=9, λ=7.14, and λ=15, and the frequency of the second resonance peak 230 is lowered, so the relatively flat bandwidth between the first resonance peak 210 and the second resonance peak 230 is reduced. When λ=15, the frequency value of the second resonance peak 230 is reduced compared to when λ=12, λ=9, or λ=7.14, so the relatively flat bandwidth between the first resonance peak 210 and the second resonance peak 230 is reduced, but the output sound pressure level is greatly improved, so it is excellent for some narrow frequency band application scenarios. Therefore, overall, λ should be a large value.

[0109] Through the design of the ratio λ, effective adjustment of the frequency value and output sensitivity of the second resonance peak 230 of the vibration assembly 100 can be realized, and the second resonance peak 230 of the vibration assembly 100 is in the range of 6000Hz to 8000Hz, and has high sensitivity. In some embodiments, the ratio λ of the height h to the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 7.14 or more. In some embodiments, more preferably, the ratio λ of the height h to the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 9 or more.

[0110] 9, the height h and thickness b of the reinforcing member 120 are both cubic parameters, and the effect on the stiffness of the reinforcing member 120 including the groove structure 121 is particularly significant. In addition, with an increase in the ratio λ of the height h to the thickness b of the reinforcing member 120 including the groove structure 121, the reinforcing member 120 can have a smaller mass and a higher stiffness, so that the vibration assembly 100 has a larger output. However, with the change in the height h and thickness b of the reinforcing member 120 including the groove structure 121, the difficulty of the process and the overall reliability of the reinforcing member 120 are affected.

[0111] As shown in Fig. 10, Fig. 10 is a frequency response curve diagram of a vibration assembly corresponding to different heights of the reinforcing member according to some embodiments of the present disclosure. As can be seen from Fig. 10, the stiffness of the reinforcing member 120 with the groove structure 121 decreases with the decrease of the height h, and the second resonance peak 230 of the vibration assembly 100 moves forward, and the sensitivity also increases accordingly. Also, the reinforcing member 120 with the groove structure 121 has excellent output when the height h is either 170 μm or 270 μm.

[0112] Designing the height h to be high is advantageous for the performance of the speaker, but as the height h of the reinforcing member 120 having the groove structure 121 increases, the difficulty of the processing process of the reinforcing member 120 (for example, chemical etching, cutter processing, laser cutting, electrochemical processing, or injection molding for nonmetallic materials, hot press molding, etc.) increases sharply. As h increases, the processing accuracy cannot be guaranteed. Considering the actual processing process, in some embodiments, the height h of the reinforcing member 120 having the groove structure 121 may be in the range of 50 μm to 500 μm. In some embodiments, in order to further reduce the difficulty of the actual processing, the height h of the reinforcing member 120 having the groove structure 121 may be in the range of 200 μm to 350 μm.

[0113] As shown in FIG. 11, FIG. 11 is a frequency response curve diagram of a vibration assembly corresponding to a reinforcing member with different thicknesses according to some embodiments of the present specification. As can be seen from FIG. 11, the reinforcing member 120 having the groove structure 121 has a reduced stiffness and reduced mass with a reduced thickness b, and the second resonance peak 230 of the vibration assembly 100 moves forward, and the sensitivity is correspondingly improved. When the thickness b of the reinforcing member 120 is large, the stiffness of the reinforcing member 120 is improved, the mass is increased, and the load formed by the reinforcing member 120 on the vibration assembly 100 is also increased, and the second resonance peak 230 moves backward, and the output sensitivity of the vibration assembly 100 is obviously reduced, for example, when the thickness b is 100 μm, the output is obviously reduced compared with the cases of other thicknesses (e.g., 20 μm, 30 μm, 50 μm, etc.); with a gradual decrease in thickness b, the second resonance peak 230 gradually moves forward, but the output sensitivity is greatly improved, which is excellent for some narrow frequency band application scenarios. Overall, the thickness b should be small.

[0114] Designing the thickness b to be small is advantageous for the performance of the speaker, but as the thickness b of the reinforcing member 120 having the groove structure 121 decreases, the reliability of the reinforcing member 120 having the groove structure 121 is significantly affected. In consideration of the reliability of the actual product, in some embodiments, the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 50 μm or less. In some embodiments, in order to make the reinforcing member 120 having the groove structure 121 have high reliability and small mass, the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 40 μm or less.

[0115] As shown in Fig. 7G, Fig. 8 and Fig. 12, Fig. 12 is a schematic diagram of a skirt structure according to some embodiments of the present specification. In Fig. 12, the shaded area represents the skirt structure. From the process perspective, the larger the design value of the width bm of the skirt structure, the larger the connection area between the reinforcing member 120 having the groove structure 121 and the central region 112 of the elastic element 110, thereby obtaining higher adhesive strength and improving the reliability of the vibration assembly 100. And the design of the width bm of the skirt structure directly determines the area of ​​the suspension region 1121 of the elastic element 110, and the equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i , etc. are determined, which further affect the location of the third resonant peak 240 of the vibrating assembly 100 and the frequency response output of the vibrating assembly 100.

[0116] As shown in FIG. 13, FIG. 13 is a frequency response curve diagram of a vibration assembly corresponding to a reinforcing member with different widths of the skirt structure according to some embodiments of the present specification. As can be seen from FIG. 13, with the increase of the width bm of the skirt structure, the output of the vibration assembly 100 obviously decreases, and the output of the third resonance peak 240 decreases. When designing the width bm of the skirt structure, the smaller the bm, the better, considering the performance. As shown in FIG. 13, when the width bm of the skirt structure is 500 μm, the output SPL obviously decreases compared with when the width bm of the skirt structure is other values ​​(e.g., 100 μm, 150 μm, 300 μm, etc.), and the process difficulty increases when the width bm of the skirt structure decreases. Based on the balance between performance and process, in some embodiments, the width bm of the skirt structure of the reinforcing member 120 having the groove structure 121 may be in the range of 100 μm to 300 μm. In some embodiments, in order to reduce the process difficulty and provide the vibration assembly 100 with excellent output performance, the width bm of the skirt structure of the reinforcing member 120 having the groove structure 121 may be in the range of 100 μm to 200 μm.

[0117] In some embodiments, when the elastic member or reinforcing member 120 in the central region 112 is connected to a driving part of a speaker, the stress and amplitude of the elastic member at the connection point are maximum, and the further away from the connection point along the extension direction from the connection point to the periphery (hereinafter referred to as the extension direction), the smaller the stress and amplitude of the elastic member. In order to accommodate the different amplitude or stress of the elastic member at each point of the central region 112, the stiffness of the reinforcing member 120 at each point in the extension direction may be different. In some embodiments, the dimensions of the elongated structure 124, the groove structure 121 of the annular structure 122 at each point in the extension direction of the reinforcing member 120 may be different, and / or the distance between adjacent groove structures 121 may be different. In some embodiments, when the central connection portion 123 is connected to a driving part of a speaker, the stiffness of the groove structure 121 gradually decreases in the extension direction from the portion close to the central connection portion 123 to the portion close to the edge region 114. For example, in the extension direction, the parameter h of the groove structure 121 gradually decreases from a portion close to the central connection 123 to a portion close to the edge region 114. For example, in the extension direction, the parameter b of the groove structure 121 gradually decreases from a portion close to the central connection 123 to a portion close to the edge region 114. Also, for example, in the extension direction, the parameter bm of the groove structure 121 gradually decreases from a portion close to the central connection 123 to a portion close to the edge region 114. In some embodiments, in the extension direction, the distance between adjacent groove structures 121 gradually increases from the distance between the groove structure 121 close to the central connection 123 and the adjacent groove structure 121 slightly away from the central connection 123 (adjacent annular structure 122) to the distance between the groove structure 121 close to the edge region 114 and the adjacent groove structure 121 slightly away from the edge region 114 (adjacent annular structure 122). The distance between adjacent groove structures 121 here is the distance between the centers (centers of gravity) of adjacent groove structures 121 (adjacent annular structures 122).

[0118] According to some embodiments herein, a manufacturing process for a reinforcing member 120 having a groove structure 121 is provided. In some embodiments, the reinforcing member 120 having a groove structure 121 may be a non-metallic material or a metallic material.

[0119] In some embodiments, the Young's modulus of the material of the reinforcing member 120 (also referred to as the reinforcing region) is higher than the Young's modulus of the material of the elastic member (also referred to as the elastic region) in order to improve the output of the vibration assembly 100 by improving the stiffness of the reinforcing member 120 and improving the elasticity of the elastic member to increase its amplitude. In some embodiments, the material of the reinforcing member 120 is different from the material of the elastic member, for example, the reinforcing member 120 is a metal material with high stiffness, and the elastic member is a non-metallic material with low stiffness. In some embodiments, the material of the reinforcing member 120 is the same as the material of the elastic member, for example, the reinforcing member 120 and the elastic member are both non-metallic materials. In this case, the reinforcing member 120 can be regarded as a structure that improves the stiffness of the elastic element 110 through structural design.

[0120] In some embodiments, the material of the reinforcing member 120 having the groove structure 121 may be a composite of one or more of the following materials: PEEK (polyether ether ketone), PI (polyimide), PEN (polyethylene naphthalate), PU (polyurethane), TPE (thermoplastic elastomer), PEI (polyetherimide), silica gel, carbon fiber, PT (polypropylene), cashmere fiber, etc. The material of the elastic element 110 may include, but is not limited to, one or more of PEEK, PI, PEN, PU, ​​PEI, silica gel. Compared with metal materials, the processing difficulty of non-metallic materials is smaller, and the processing uniformity is more easily ensured.

[0121] In some embodiments, the vibration assembly is manufactured by the following steps: manufacturing a groove structure and an openwork structure on the reinforcing member; and connecting the reinforcing member and the elastic element to manufacture the vibration assembly. In some embodiments, the groove structure is manufactured by a first process. In some embodiments, the first process may include one or more of injection molding, hot press molding, etching, cutting, laser cutting, and electrochemical processing. In some embodiments, the openwork structure may be manufactured by a second process. In some embodiments, the second process may include laser cutting. In some embodiments, the groove structure and the openwork structure may be manufactured by an integral molding process. In some embodiments, after manufacturing the reinforcing member, an adhesive may be applied (e.g., an adhesive adhesive is sprayed) on the reinforcing member or the elastic element, and then the reinforcing member and the elastic element may be connected by hot press molding to manufacture the vibration assembly.

[0122] As shown in Figures 14A and 14B, Figure 14A is a schematic diagram showing a manufacturing process of a non-metallic reinforcement member and vibration assembly according to some embodiments of the present specification, and Figure 14B is a schematic diagram of a model corresponding to Figure 14A. In some embodiments, when the material of the reinforcement member 120 (also called the reinforcement region) is the same as the material of the elastic member (also called the elastic region), the reinforcement member 120 can use a non-metallic material, and for the reinforcement member 120 having the groove structure 121 made of a non-metallic material, the processing process may include the following steps 1410 to 1430.

[0123] In step 1410, molding is performed using a hot press mold.

[0124] In some embodiments, the reinforcing member 120 may be manufactured by molding using a hot press mold. For example, after processing the processing mold, a liquid sample is injected or a solid sample is put in, the mold is fixed on a hot plate by solid contact pressure or gas pressure, the melting temperature and time of the sample are controlled, the sample is melted and then hardened, cooled, and the finished product in the mold is removed to obtain the initial reinforcing member 120. In some embodiments, the reinforcing member 120 may be manufactured by other processes capable of processing non-metallic materials, which are not described herein. In some embodiments, the groove structure 121 may be directly formed (i.e., the groove is formed in the reinforcing member 120) by placing a corresponding mold during the hot press molding process using a mold. In some embodiments, the reinforcing member 120 may have the groove structure 121 by removing the material of a given area of ​​the reinforcing member 120 by laser engraving to form a groove. In some embodiments, the reinforcing member 120 may have the groove structure 121 by other processes such as etching, which are not described herein.

[0125] In step 1420, laser engraving is performed.

[0126] In some embodiments, laser engraving can be used to remove material in given areas of the reinforcement member 120 to form the openwork structure. In some embodiments, other processes, such as etching, can be used to form the openwork structure in the reinforcement member 120 and are not discussed herein.

[0127] At step 1430, the connection is made and the molded.

[0128] In some embodiments, the reinforcing member 120 having the groove structure 121 and the elastic element 110 can be connected and finally molded. In some embodiments, the surface of the elastic element 110 or the reinforcing member 120 can be sprayed with an adhesive, and then the elastic element 110 and the reinforcing member 120 can be connected by hot press molding. In some embodiments, the elastic element 110 and the reinforcing member 120 can be directly connected by hot press without applying adhesive between them. In some embodiments, the reinforcing member 120 can be connected and fixed to the elastic element 110 by other methods, which will not be described in this specification.

[0129] In some embodiments, the material of the reinforcing member 120 may include, but is not limited to, aluminum alloys, copper and its alloys, stainless steel, gold and its alloys, tungsten, etc. Compared to non-metallic materials, the reinforcing member 120 made of metallic materials has higher stiffness for the same mass, which can improve the output of the vibrating assembly 100.

[0130] As shown in Figures 15A and 15B, Figure 15A is a schematic diagram illustrating a manufacturing process of a metallic reinforcement member and a vibration assembly according to some embodiments of the present specification, and Figure 15B is a schematic diagram of a model corresponding to Figure 15A. In some embodiments, when the material of the reinforcement member 120 (also called the reinforcement region) is different from the material of the elastic member (also called the elastic region), the reinforcement member 120 can use a metallic material, and for the reinforcement member 120 having a groove structure 121 made of a metallic material, the processing process generally includes the following steps 1510 to 1530.

[0131] In step 1510, processing and molding is performed.

[0132] In some embodiments, machining may include one or more processes capable of processing metallic materials, such as chemical etching, cutting, laser cutting, electrochemical machining, and the like.

[0133] In step 1520, laser engraving is performed.

[0134] In some embodiments, step 1520 may be the same as step 1420 and will not be described here.

[0135] In some embodiments, step 1520 can be performed simultaneously with step 1510 , ie, the groove structure 121 of the reinforcing member 120 can be integrally molded directly with the reinforcing member 120 .

[0136] At step 1530, the connection is made and the molded.

[0137] In some embodiments, step 1530 may be the same as step 1430 and will not be described here.

[0138] In some embodiments, the relationship between the area of ​​the suspension region 1121 and the edge region 114 and the thickness of the elastic element 110 is determined by the local equivalent mass Mm 3 , local equivalent mass Mm 2 , local area stiffness Ka' 2 and local area stiffness Ka' 1 , thereby controlling the range of the second resonant peak 230 of the vibrating assembly 100.

[0139] As shown in FIG. 16, FIG. 16 is a schematic diagram of a vibration assembly having a reinforcing member of a single ring structure according to some embodiments of the present disclosure. In some embodiments, the reinforcing member 120 includes a central connection 123 and an elongated structure 124, the elongated structure 124 extends from the central connection 123 of the reinforcing member 120 to the periphery, and the groove structure 121 is disposed on the transverse surface of the elongated structure 124. The horizontal projection area of ​​the suspension region 1121 is S. v and the horizontal plane projection area of ​​the edge region 114 is defined as S e and the horizontal plane projection area S of the suspension area 1121 is defined as v and the horizontal plane projection area S of the edge region 114 e The sum of these is S s The physical quantity α (unit: mm) is defined as S s and the thickness of the elastic element 110 (also called the vibration film thickness) H iIt is defined as the ratio of

[0140] α=S s / H i (Formula 3)

[0141] In some embodiments, to place the second resonant peak 230 in the range of 5000 Hz to 10000 Hz, S s and the thickness of the diaphragm H i The ratio α may be in the range of 5000 mm to 12000 mm. In some embodiments, to set the second resonant peak 230 in the range of 6000 Hz to 9000 Hz, α may be in the range of 6000 mm to 10000 mm. In some embodiments, to set the second resonant peak 230 in the range of 6000 Hz to 8500 Hz, α may be in the range of 6000 mm to 9000 mm. In some embodiments, to set the second resonant peak 230 in the range of 6000 Hz to 8000 Hz, α may be in the range of 6000 mm to 8000 mm. In some embodiments, to set the second resonant peak 230 in the range of 6000 Hz to 7500 Hz, α may be in the range of 6000 mm to 7000 mm. In some embodiments, α may be in the range of 7000 mm to 9000 mm to bring second resonant peak 230 in the range of 7000 Hz to 8500 Hz. In some embodiments, α may be in the range of 7000 mm to 8000 mm to bring second resonant peak 230 in the range of 7000 Hz to 8000 Hz.

[0142] In some embodiments, the three-dimensional dimensions of the edge region 114 of the elastic element 110 are changed by designing the edge arch height of the edge region 114 to change the stiffness Ka′ of the edge region 114 while keeping the horizontal projected area of ​​the edge region 114 and the horizontal projected area of ​​the suspension region 1121 of the vibration assembly 100 unchanged. 1 can be varied, further controlling the second resonant peak of the vibrating assembly 100.

[0143] As shown in FIG. 17, FIG. 17 is a partial schematic diagram of a vibration assembly according to some embodiments of the present specification. In this specification, the arch height of the edge of the edge region 114 is defined as Δh, and the physical quantity δ (unit: mm) is defined as S s and the arch height Δh of the edge of the diaphragm.

[0144] δ = S s / Δh (Equation 4)

[0145] In some embodiments, δ may be in the range of 50 mm to 600 mm. In some embodiments, δ may be in the range of 100 mm to 500 mm to ensure that the edge region 114 has suitable three-dimensional dimensions. Preferably, δ may be in the range of 200 mm to 400 mm. More preferably, δ may be in the range of 250 mm to 400 mm. In some embodiments, δ may be in the range of 250 mm to 350 mm to ensure that the edge region 114 has suitable rigidity. Preferably, δ may be in the range of 250 mm to 300 mm. More preferably, δ may be in the range of 200 mm to 300 mm.

[0146] In some embodiments, the horizontal projection area of ​​the maximum contour of the reinforcing member 120 (i.e., the size of the outermost annular structure 122) is set to adjust the size (or area) of the suspension region 1121 between the edge region 114 and the reinforcing member 120 to reduce the equivalent mass Mt 1 and equivalent stiffness Kt 1 , which further controls the range of the second resonant peak 230 of the vibrating assembly 100.

[0147] In this specification, the horizontal projection area of ​​the central region 112 is S c and the horizontal projection area of ​​the maximum contour of the reinforcing member 120 is defined as S rm and the horizontal plane projection area of ​​the suspension area 1121 is defined as S v Define S rm =S c -S v .

[0148] In this specification, physical quantities,

[0149]

number

[0150] (Unit: 1) is the horizontal projection area S of the suspension area 1121 v and the horizontal projection area S of the central region 112 c It is defined as the ratio of

[0151]

number

[0152] =S v / S c (Formula 5)

[0153] In some embodiments,

[0154]

number

[0155] In some embodiments, in order to ensure that the suspension region 1121 has a suitable area,

[0156]

number

[0157] is in the range of 0.1 to 0.5.

[0158]

number

[0159] is in the range of 0.15 to 0.35. More preferably,

[0160]

number

[0161] In some embodiments, the equivalent mass Mt 1 and equivalent stiffness Kt 1 To ensure that has the appropriate value,

[0162]

number

[0163] is in the range of 0.2 to 0.5.

[0164]

number

[0165] is in the range of 0.15 to 0.25. More preferably,

[0166]

number

[0167] is in the range of 0.15 to 0.2.

[0168] In some embodiments, the elongated structures 124 can have different widths, shapes and numbers to adjust the frequency of the speaker's frequency response by changing the openwork area (the suspension area corresponding to the central area 112) of the reinforcing member 120. For specific details, please refer to the following Figures 20 to 25E and their related descriptions.

[0169] In some embodiments, by designing the area of ​​the openwork region (e.g., by designing the number and position of the elongated structures 124 of the reinforcing member 120, the number and position of the annular structures 122, etc.), the resonant frequency of the vibrating assembly 100 can be adjusted to improve the usage performance of the vibrating assembly 100.

[0170] As shown in Fig. 5A and Fig. 18, Fig. 18 is a deformation diagram of the CC cross section of the vibration assembly according to some embodiments of the present specification near the frequency of the third resonance peak. As can be seen from Fig. 5A, the frequency difference between the third resonance peak 240 and the second resonance peak 230 has a large effect on the flatness of the frequency response curve of the high frequency band of the vibration assembly 100. In some embodiments, as can be seen from the vibration situation in the CC cross section of the vibration assembly 100 as shown in Fig. 18, near the frequency of the third resonance peak, the main deformation position of the vibration assembly 100 is the part of the deformation generated in the openwork area of ​​the central area 112. In some embodiments, it becomes a mass-spring-damping system, and the equivalent mass Mm i , equivalent stiffness Ka i The third resonant peak 240 of the vibrating assembly 100 can be controlled by controlling each openwork area corresponding to the central region 112 of the stiffening member 120 to correspond to S. For example, the number and dimensions of the elongated structures 124 and the annular structures 122 can be designed to design the area of ​​each openwork area of ​​the central region 112, and the area of ​​each openwork area can be set to S. i It should be noted that although Fig. 18 shows a deformation diagram at the third resonance peak of the vibration assembly 100 having a single ring-shaped reinforcing member 120, the conclusion still applies to vibration assemblies having multiple ring-shaped reinforcing members 120.

[0171] In order to set the third resonance peak in an appropriate frequency range (12000 Hz to 18000 Hz), in this specification, the physical quantity is defined as the area S of any openwork region. i and the thickness H of the diaphragm of each openwork area i The area-to-thickness ratio μ (unit: mm) is defined as the ratio of

[0172] μ = S i / H i (Formula 6)

[0173] By designing μ, the frequency location of the third resonant peak of the vibrating assembly can be adjusted.

[0174] In some embodiments, the area-to-thickness ratio μ is in the range of 100 to 1000. In some embodiments, each openwork region has a corresponding suitable equivalent mass Mm i and equivalent stiffness Ka i In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 700 so that each openwork region has a corresponding appropriate equivalent mass Mm i and equivalent stiffness Ka i In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 950 so that each openwork region has a corresponding appropriate equivalent mass Mm i and equivalent stiffness Ka i In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 900. In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 800. In some embodiments, each openwork region has a corresponding appropriate equivalent mass Mm i and equivalent stiffness Ka i In order to have such a property, the area-to-thickness ratio μ is in the range of 100 to 700. Preferably, the area-to-thickness ratio μ is in the range of 300 to 500. More preferably, the area-to-thickness ratio μ is in the range of 400 to 600.

[0175] It should be noted that although the structure shown in FIG. 18 is a single ring structure, the above range of area thickness ratio μ still applies for multiple ring structures.

[0176] As shown in FIG. 19, in some embodiments, the reinforcing member 120 has a double annular structure, and the area of ​​each openwork region of the elastic element 110 inside the first annular structure is defined as S 1i and the area of ​​each openwork region of the elastic element 110 between the first annular structure and the second annular structure is defined as S 2i In some other embodiments, the reinforcing member 120 may have more annular structures 122, and the area of ​​each openwork region of the elastic element 110 between the (n-1)th annular structure and the (n)th annular structure is defined as S niIn this specification, the physical quantity of the openwork area ratio γ (unit: 1) of the elastic element 110 is defined as the ratio of the area S of any two openwork areas ki and S. ji It is defined as the ratio of

[0177] γ=S ki / S ji (Formula 7)

[0178] where k>j. By designing γ, the frequency location of the third resonant peak of the vibrating assembly can be adjusted.

[0179] As shown in FIG. 19 and FIG. 20, FIG. 20 is a frequency response curve of the vibration assembly corresponding to FIG. 19. In the structures 1 to 4, the area S of each openwork area between the first annular area and the second annular area is 2i and the area S of each openwork area inside the first annular area 1i The area ratios γ of the central region 112 and the openwork region 122 are 5.9, 4.7, 3.9, and 3.2, respectively. As can be seen from FIG. 19, in the third resonance peak position of the vibration assembly 100, in the structures 1 to 4, with the decrease of γ, the radius ΔR1 of the first openwork region located in the inner annular structure 122 gradually increases, and the radius ΔR2 of the second openwork region located between the inner annular structure 122 and the outer annular structure 122 gradually decreases. In some embodiments, as further shown in FIG. 20, in the frequency response curves of the vibration assemblies of the structures 1 to 4, the sound pressure amplitude output at the third resonance peak position gradually increases. Therefore, the area ratios of each openwork region of the central region 112 affect the resonance frequency of each openwork region, and finally obtain the sound pressure superposition effect in the high frequency band, that is, by setting γ, the high frequency sensitivity of the vibration assembly 100 can be adjusted.

[0180] In some embodiments, as can be seen from FIG. 20, as γ gradually decreases, the third resonance peak appears prominently and the output sound pressure level of the corresponding frequency band increases, and when γ is 5.9 (corresponding to structure 1), the third resonance peak is not formed and the output sound pressure level of the frequency band decreases significantly, and the output of the frequency band of the third resonance peak is significantly improved compared to when γ is 4.7 or less (e.g., γ=4.7 corresponding to structure 2, γ=3.9 corresponding to structure 3, and γ=3.2 corresponding to structure 4). In some embodiments, the area S of any two openwork regions is ki and S. ji In some embodiments, to further improve the high frequency sensitivity of the vibrating assembly 100, the ratio γ of the areas S of any two openwork regions is ki and S. ji In some embodiments, to further improve the high frequency sensitivity of the vibrating assembly 100, the ratio γ of the areas S of any two openwork regions is ki and S. ji In some embodiments, the ratio γ of the areas S of any two openwork regions is in the range of 3.5 or less. ki and S. ji In some embodiments, to further improve the high frequency sensitivity of the vibrating assembly 100, the ratio γ of the areas S of any two openwork regions is ki and S. ji The ratio γ is in the range of 3 or less.

[0181] In some embodiments, by designing the projected area of ​​the reinforcing member 120 along the vibration direction and the projected area of ​​the maximum contour of the reinforcing member 120 onto the central region 112 along the vibration direction, it is possible to adjust the mass, center of mass, stiffness of the reinforcing member 120, and the mass and stiffness of the suspension region of the central region 112, thereby enabling adjustment of the first resonant peak, the second resonant peak, and the third resonant peak of the vibration assembly 100.

[0182] In order to facilitate the design of the reinforcing member 120, in this specification, as shown in FIG. 19, the lateral area ratio β (unit: 1) of the groove structure of the reinforcing member 120 to the reinforcing member 120 is defined as the projection area S of the groove structure in a projection along the vibration direction of the reinforcing member 120. r and the projected area S of the maximum contour of the reinforcing member 120 onto the central region 112 t It is defined as the ratio of

[0183] β=S r / S t (Formula 8)

[0184] In some embodiments, the projection of the reinforcing member 120 along the vibration direction is the projection of the groove structure of the reinforcing member 120. The projection of the maximum contour of the reinforcing member 120 coincides with the projection of the central region 112.

[0185] As shown in FIG. 21, FIG. 21 is another frequency response curve diagram of a vibration assembly according to some embodiments of the present disclosure. As can be seen from FIG. 21, the projected area S r and the projected area S of the maximum contour of the reinforcing member 120 t With the change in the ratio β, the output of the third resonance peak of the speaker also changes obviously. When the ratio β is small, the equivalent stiffness Ka' i The equivalent mass Mm i increases, the third resonance peak moves forward, and when the ratio β is large, the equivalent stiffness Ka' i The equivalent mass Mm i is reduced and the third resonance peak moves backward.

[0186] By designing β, the equivalent stiffness Ka' i and equivalent mass Mm i can be adjusted to make the high-frequency third resonance peak of the vibration assembly in a suitable frequency range, and make the resonance frequency difference of each openwork structure in a suitable range (for example, 4000 Hz or less). In some embodiments, the lateral area ratio β of the groove structure of the reinforcing member 120 to the reinforcing member 120 is 0.15 to 0.8. Preferably, the lateral area ratio β of the groove structure of the reinforcing member 120 to the reinforcing member 120 is 0.35 to 0.65.

[0187] As shown in Figures 22A and 22B, Figures 22A and 22B are schematic diagrams of vibration assemblies with different numbers of elongated structures according to some embodiments of the present disclosure. In some embodiments, by adjusting the number of elongated structures 124, the mass of the entire vibration assembly 100 can be adjusted to change the total equivalent mass Mt formed by combining the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent driving end mass, so that the resonance frequency of the formed mass Mt-spring Kt-damping Rt system changes, which in turn changes the primary resonance frequency of the vibration assembly 100, and changes the sensitivity of the low frequency band before the first resonance frequency of the vibration assembly 100 and the mid frequency band after the first resonance frequency. In some embodiments, more elongated structures 124 may be designed to increase the total equivalent mass Mt, and the first resonant frequency of the vibrating assembly 100 may be moved forward to improve the sensitivity of low frequency bands before the first resonant frequency of the vibrating assembly 100, for example, frequency bands before 3000 Hz, frequency bands before 2000 Hz, frequency bands before 1000 Hz, frequency bands before 500 Hz, and frequency bands before 300 Hz. In some embodiments, fewer elongated structures 124 may be designed to decrease the total equivalent mass Mt, and the first resonant frequency of the vibrating assembly 100 may be moved backward to improve the sensitivity of mid frequency bands after the first resonant frequency of the vibrating assembly 100, for example, frequency bands after 3000 Hz. Also, for example, the sensitivity of frequency bands after 2000 Hz may be improved. Also, for example, the sensitivity of frequency bands after 1000 Hz may be improved. Also, for example, the sensitivity of frequency bands after 500 Hz may be improved. Also, for example, the sensitivity of the frequency band after 300 Hz may be increased.

[0188] In some embodiments, adjusting the number of elongated structures 124 can further adjust the stiffness of the stiffening member 120 to reduce the stiffness Kt provided to the system by the stiffening member 120 and the elastic element 110. 1can be varied, and the stiffening member 120, the connection region 115, the edge region 114, the suspension region between the region of the central region 112 surrounded by the stiffening member 120 and the edge region 114, the equivalent air mass, and the driving end equivalent mass can be combined to produce a total equivalent mass Mt 1 The equivalent damping of each part forms the total equivalent damping Rt 1 and the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 The system uses an annular region in the diameter direction of the stiffening member 120 as an equivalent fixed support and changes the resonant frequency of the inversion motion of the ring, thereby varying the second resonant position of the vibrating assembly 100.

[0189] In some embodiments, the number of elongated structures 124 may be adjusted, and the area of ​​one or more suspension regions corresponding to the central region 112 of the reinforcing member 120 may be adjusted to reduce the equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i can be varied, thereby varying the location of the third resonant peak of the vibrating assembly. In some embodiments, by adjusting the number of elongated structures 124, the area-to-thickness ratio μ of the vibrating assembly and the lateral area ratio β of the groove structure of the stiffening member 120 to the stiffening member 120 can be further adjusted to adjust the location of the third resonant peak of the vibrating assembly.

[0190] In some embodiments, the number of elongated structures 124 of the reinforcing member 120 is adjustable, and the positions of the first resonant peak, the second resonant peak, and the third resonant peak of the vibration assembly 100 can be adjusted according to actual application needs, thereby realizing controllable adjustment of the frequency response of the vibration assembly 100.

[0191] In some embodiments, the shape of the projection of the elongated structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape, so that by adjusting the shape of the elongated structure 124, the area of ​​the openwork area of ​​the reinforcing member 120 (corresponding to the suspension area of ​​the central region 112 within the projection range of the reinforcing member 120) can be changed to adjust the relationship (area-thickness ratio μ) between the area of ​​the openwork area and the thickness of the elastic element 110, thereby achieving the purpose of adjusting the third resonant peak. By changing the area relationship of the openwork areas between different annular structures 122 of the reinforcing member 120 (openwork area area ratio γ), the objective of adjusting the third resonant peak can be achieved, and further, by changing the relationship between the lateral area of ​​the groove structure of the reinforcing member 120 and the reinforcing member 120 (lateral area ratio β between the groove structure of the reinforcing member 120 and the reinforcing member 120), the objective of adjusting the first resonant peak, the second resonant peak, and the third resonant peak can be achieved.

[0192] 23A-23D, which are schematic diagrams of vibrating assemblies having elongated structures with different widths according to some embodiments herein, the elongated structures 124 in FIG. 23A are inverted trapezoids (i.e., the short side of the trapezoid is close to the center of the stiffening member 120), the elongated structures 124 in FIG. 23B are trapezoids (i.e., the short side of the trapezoid is away from the center of the stiffening member 120), the elongated structures 124 in FIG. 23C are outwardly arced, and the elongated structures 124 in FIG. 23D are inwardly arced. In some embodiments, the location of the center of mass of the stiffening member 120 can be effectively adjusted by designing the elongated structures 124 with different lateral widths. In some embodiments, the stiffness of the reinforcing member 120 itself may be changed without changing the mass of the reinforcing member 120, thereby reducing the stiffness Kt provided to the system by the reinforcing member 120, the elastic element 110 (particularly the area of ​​the central region 112 covered by the reinforcing member 120). 1 changes, and the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1By varying the resonant frequency of the reciprocating motion of the system, the second resonant frequency of the vibrating assembly 100 is changed.

[0193] In some embodiments, the design of the width of the elongated structure 124 can be varied to allow for different local stiffness at different locations extending from the center to the periphery of the elongated structure 124. 1 -Spring Kt 1 -Attenuation Rt 1 When close to the resonant frequency of the system, the connection region 115 between the fixed region 116 and the edge region 114, the edge region 114, and the suspension region between the area of ​​the central region 112 covered by the reinforcing member 120 and the edge region 114 are driven by the reinforcing member 120 to vibrate, resulting in a resonant peak that is adjustable with a 3 dB bandwidth.

[0194] As shown in Figures 23A to 23D, in some embodiments, the long-length structure 124 is designed to have an inverted trapezoidal shape, an outer arc shape (an arc shape that protrudes outward is defined as an outer arc shape, and an arc shape that concaves inward is defined as an inner arc shape, and the outer arc shape may be a circular arc, an ellipse, a high-order function arc, and any other outer arc shape), so that the second resonance peak of the vibration assembly 100 with a wide 3 dB bandwidth can be obtained, and it can be applied to scenarios where a low Q value and a wide bandwidth are required. In some embodiments, the long-length structure 124 is designed to have a trapezoidal shape, a rectangular shape, and an inner arc shape (an arc shape that protrudes outward is defined as an outer arc shape, and an arc shape that concaves inward is defined as an inner arc shape, and the inner arc shape may be a circular arc, an ellipse, a high-order function arc, and any other inner arc shape), so that the second resonance peak of the vibration assembly 100 with a high sensitivity and a small 3 dB bandwidth can be obtained, and it can be applied to scenarios where a high Q value and a high local sensitivity are required.

[0195] By designing the elongated structures 124 with different lateral widths, it is possible to further adjust the area of ​​one or more suspension regions corresponding to the central region 112 of the stiffening member 120, thereby adjusting the area of ​​each equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Rai , Ra' i In addition, the third resonant peak position of the vibrating assembly 100 changes.

[0196] Therefore, by designing the elongated structures 124 with different lateral widths, the frequency location of the second resonant peak of the vibrating assembly 100, the 3 dB bandwidth at the resonant peak, the sensitivity of the vibrating assembly 100 at the resonant peak, and the location of the third resonant peak of the vibrating assembly 100 can be achieved.

[0197] 24A and 24B, which are schematic diagrams of vibrating assemblies having different shapes of elongated structures according to some embodiments herein, in which the elongated structure 124 in FIG. 24A is a rotational shape, and in FIG. 24B the elongated structure 124 is an S-shape. In some embodiments, by designing the elongated structures 124 with different lateral shapes, the stiffness of the stiffening member 120 can be adjusted to reduce the stiffness Kt provided to the system by the stiffening member 120, the elastic element 110 (especially the area covered by the stiffening member 120 in the central region 112). 1 and change the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 By changing the resonant frequency of the reciprocating motion of the system, the second resonant position of the vibrating assembly 100 is changed. In some embodiments, the area of ​​one or more suspension regions corresponding to the central region 112 of the stiffening member may be further adjusted to change the second resonant position of each equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i , which changes the third resonance peak position of the vibrating assembly 100. In some embodiments, the stress distribution within the stiffening member 120 can be further adjusted and the processing deformation of the stiffening member 120 can be controlled by designing the elongated structures 124 with different lateral shapes.

[0198] As shown in FIG. 25A-25E, FIG. 25A-25E are schematic diagrams of reinforcing members having elongated structures of different shapes according to some embodiments of the present disclosure. In some embodiments, in order to precisely adjust the effect of elongated structures of different shapes on the resonant peaks (e.g., the first resonant peak, the second resonant peak, and the third resonant peak) of the vibrating assembly, the included spoke angle is defined as θ for the elongated structure 124 whose width gradually decreases from the center to the edge, and the included angle θ can be adjusted to adjust the resonant peak of the vibrating assembly. In some embodiments, in the case of the elongated structure 124 whose sides are straight sides (as shown in FIG. 25A-25D), the included angle θ is the included angle between the two sides of the spoke. In some embodiments, in the case of the elongated structure 124 whose sides are arc sides (as shown in FIG. 25E), the included angle θ is the included angle between the tangents of the two sides of the elongated structure 124. In some embodiments, to precisely tailor the effect of differently shaped elongated structures on the resonant peaks (e.g., the first resonant peak, the second resonant peak, and the third resonant peak) of the vibrating assembly, the included spoke angle may be set to θ for a spoke structure that gradually increases in width from the center to the edge, as shown in FIG. 25D. i Define θ i In some embodiments, for an elongated structure 124 with straight sides, the included angle θ i is the included angle between the two sides of the spoke. In some embodiments, for elongated structures 124 whose sides are arcs, the included angle θ i is the included angle between the tangents to the two sides of the spoke.

[0199] In some embodiments, the included angle θ (or θ i ) is designed to change the stiffness of the reinforcing member 120 itself while keeping the mass of the reinforcing member 120 unchanged or changed, thereby changing the stiffness Kt provided to the system by the reinforcing member 120 and the elastic element 110. 1 changes, and the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1By changing the resonant frequency of the reversible motion of the system, the second resonant position of the vibrating assembly 100 can be changed and the 3 dB bandwidth of the second resonant peak of the vibrating assembly 100 can be controlled. In some embodiments, the included angle θ (or θ i ) can effectively increase the 3 dB bandwidth of the third resonant peak of the vibrating assembly 100.

[0200] In order to accommodate the frequency response of some vibrating assemblies 100 that require a low Q and a wide bandwidth, the included angle θ (or θ i ) can be designed to be large. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 150°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 120°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 90°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0° to 60°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0° to 60°. i may range from 0 to 90 degrees. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 70°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 45°.

[0201] In response to the frequency response of some vibrating assemblies 100 requiring a high Q and narrow bandwidth, the included angle θ (or θ i) can be designed to be small. In some embodiments, the included angle θ of the elongated structures 124 may be in the range of 0 to 90°. In some embodiments, the included angle θ of the elongated structures 124 may be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structures 124 may be in the range of 0 to 70°. In some embodiments, the included angle θ of the elongated structures 124 may be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structures 124 may be in the range of 0 to 45°. In some embodiments, the included angle θ of the elongated structures 124 i may range from 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 90 degrees. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 120°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 150°.

[0202] In some embodiments, θ and θ i The relationship between is defined as follows:

[0203] θ=-θi (Equation 9)

[0204] The included angle θ of the elongated structure 124 can be designed to be large to accommodate some loudspeaker frequency responses that require a low Q value and a wide bandwidth. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of -90° to 150°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of -45° to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0° to 60°.

[0205] In order to accommodate some loudspeaker frequency responses that require a high Q factor and narrow bandwidth, the included angle θ of the elongated structure 124 can be designed to be small. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of -150° to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of -90° to 45°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of -60° to 0°.

[0206] In some embodiments, for irregularly shaped elongated structures 124, the included angle of the elongated structure 124 cannot be designed. In this case, the method of area can be used to design, and the stiffness Kt provided to the system by the reinforcing member 120, the elastic element 110, and the stiffness of the reinforcing member 120 itself can be varied while keeping the mass of the reinforcing member 120 unchanged or varied. 1 changes, and the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 By varying the resonant frequency of the reversal motion of the system, the second resonant position of the vibrating assembly 100 can be varied, and further the 3 dB bandwidth of the second resonant peak of the vibrating assembly 100 can be controlled.

[0207] 26A and 26B, which are schematic diagrams of a reinforcing member having an irregular elongated structure according to some embodiments of the present disclosure. In some embodiments, in order to precisely design the irregular elongated structure to adjust the resonance peak of the vibration assembly, as shown in FIG. 26A, a circle with a radius R is defined by the maximum contour of the reinforcing member 120, and 1 / 2 of the radius R of the circle defined by the maximum contour is defined as radius R / 2, and the horizontal projection area of ​​the reinforcing member 120 within the radius R / 2 range is defined as radius S. in and the horizontal projection area (i.e., the projection along the vibration direction of the vibrating assembly) of the reinforcement member 120 within the range between the circle of radius R / 2 and the circle of radius R is defined as S out and the physical quantity τ is defined as the horizontal projection area S of the reinforcing member 120. out and the horizontal projection area S of the reinforcing member 120 inIt is defined as the ratio of

[0208] τ=S out / S in (Formula 10)

[0209] In some embodiments, the horizontal projection area S of the reinforcing member 120 may be out and the horizontal projection area S of the reinforcing member 120 in By adjusting the ratio τ of τ to τ, the mass distribution of the reinforcing member 120 can be controlled, thereby realizing the control of the bandwidth of the third resonance peak of the vibrating assembly 100. In the case of other types of regular reinforcing member 120 structures, for example, elliptical, rectangular, square, and other polygonal structures as shown in FIG. 26B, a figure similar to the reinforcing member 120 is defined and enveloped by the maximum outline of the reinforcing member 120, and the central region of the figure is defined as a reference point, and the distance from the reference point to each point on the outline envelope is R (as shown in FIG. 26B, the distances from the reference point to the four sides of the rectangular outline envelope are R, respectively). i , R i+1 , R i+2 , R i+3 ), and all corresponding R / 2 (as shown in FIG. 26B, the distance is R i / 2, R i+1 / 2, R i+2 / 2, R i+3 The horizontal projection area of ​​the reinforcing member 120 in the region formed by the points (points S1 / S2) is defined as S in The horizontal projection area of ​​the reinforcing member 120 within the range between the distance R / 2 and the distance R is S out In the case of another irregular structure of the reinforcing member 120, the maximum contour of the reinforcing member 120 is enveloped by a regular shape of a structure more similar to the maximum contour of the reinforcing member 120, and S in , S out , and define the ratio τ.

[0210] In response to some frequency responses of the vibrating assembly 100 requiring a low Q value and a wide bandwidth, the stiffening member 120 can be designed to have a large mass concentrated in a central region. In some embodiments, to increase the mass of the central region of the stiffening member 120, the horizontal projection area S out and horizontal projection area S inThe ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.3 to 2. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.5 to 1.5. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.5 to 1.2. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.5 to 1.3. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.5 to 1.4. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.3 to 1.2. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.3 to 1.6. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.5 to 2. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.5 to 2.2. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the central region of the reinforcing member 120 may be in the range of 0.3 to 2.2. out and horizontal projection area Sin The ratio τ may be in the range of 0.3 to 2.

[0211] In response to some vibrating assemblies 100 requiring high Q and narrow bandwidth frequency responses, the stiffening member 120 can be designed to have a large concentrated mass at the edge region. In some embodiments, to increase the mass at the edge region of the stiffening member 120, the horizontal projected area S out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may range from 1 to 3. In some embodiments, to increase the mass of the edge region of the reinforcing member 120, out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the edge area S may be in the range of 1.2 to 2.8. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.4 to 2.6 in order to increase the mass of the edge region of the reinforcing member 120. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.6 to 2.4 in order to increase the mass of the edge region of the reinforcing member 120. out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.8 to 2.2 in order to increase the mass of the edge region of the reinforcing member 120. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.2 to 2. In some embodiments, to increase the mass of the edge region of the reinforcing member 120, out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may range from 1 to 2. In some embodiments, to increase the mass of the edge region of the reinforcing member 120, out and horizontal projection area S in In some embodiments, the ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 2 to 2.8 in order to increase the mass of the edge region of the reinforcing member 120.out and horizontal projection area S in The ratio τ may be in the range of 2 to 2.5.

[0212] In some embodiments, the purpose of adjusting the third resonance peak can be achieved by adjusting the number of annular structures 122 (in the range of 1 to 10) and changing the area of ​​the openwork area (the suspension area corresponding to the central area 112 within the projection range of the reinforcing member 120) of the reinforcing member 120 to adjust the relationship between the area of ​​the openwork area and the thickness of the elastic element 110 (area-thickness ratio μ); the purpose of adjusting the third resonance peak can be achieved by changing the area relationship between the openwork areas of different annular structures 122 of the reinforcing member 120 (openwork area area ratio γ); and the purpose of adjusting the first resonance peak, the second resonance peak, and the third resonance peak can be achieved by changing the relationship between the lateral area of ​​the groove structure of the reinforcing member 120 and the reinforcing member 120 (lateral area ratio β between the groove structure of the reinforcing member 120 and the reinforcing member 120).

[0213] In some embodiments, the annular structure 122 may include a first annular structure and a second annular structure with overlapping centers of gravity, where the radial dimension of the first annular structure is smaller than the radial dimension of the second annular structure. In some embodiments, the elongated structure 124 may further include at least one first elongated structure and at least one second elongated structure, where the at least one first elongated structure is disposed inside the first annular structure and connected to the first annular structure, and the at least one second elongated structure is disposed between the first annular structure and the second annular structure and connected to the first annular structure and the second annular structure, respectively, to form a plurality of distinct openwork regions in the reinforcing member 120.

[0214] As shown in FIG. 27A-27C, FIG. 27A-27C are schematic diagrams of vibration assemblies having different numbers of annular structures according to some embodiments herein, where the annular structure 122 in FIG. 27A is a single annular structure, the annular structure 122 in FIG. 27B is a double annular structure, and the annular structure 122 in FIG. 27C is a triple annular structure. By designing the number of annular structures 122, the mass and stiffness of the reinforcing member 120 can be adjusted, and the area of ​​the openwork region of the central region 112 can be adjusted. In some embodiments, the number of annular structures 122 can be in the range of 1-10. In some embodiments, the number of annular structures 122 can be in the range of 1-5. In some embodiments, the number of annular structures 122 can be in the range of 1-3.

[0215] In some embodiments, by adjusting the number of annular structures 122, the mass of the reinforcing member 120 can be adjusted to change the total equivalent mass Mt formed by combining the mass of the reinforcing member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent driving end mass, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibrating assembly 100.

[0216] In some embodiments, adjusting the number of annular structures 122 may further adjust the stiffness of the reinforcing member 120 to reduce the stiffness, Kt, provided to the system by the reinforcing member 120, the elastic element 110 (especially the area of ​​the central region 112 covered by the reinforcing member 120). 1 can be changed, and the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 The resonant frequency of the reversible motion of the system is changed, thereby changing the second resonant position of the vibrating assembly 100. In some embodiments, adjusting the number of annular structures 122 can further vary the stiffness distribution at different positions extending from the center of the elongated structure 124 to the periphery, thereby changing the drive end frequency relative to the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1When close to the resonant frequency of the system, the connection region 115, the edge region 114, and the local suspension region between the area covered by the reinforcing member 120 in the central region 112 and the edge region 114 are driven by the reinforcing member 120 to vibrate, resulting in a tunable resonant peak with a 3 dB bandwidth.

[0217] In some embodiments, the number of annular structures 122 can be adjusted, and the area of ​​the openwork regions in the central region 112 can be adjusted to adjust the equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i can be varied, thereby changing the third resonant peak position of the vibrating assembly 100.

[0218] In some embodiments, by adjusting the number of annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness H of the diaphragm of each openwork area i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 150 to 700. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the lateral area ratio β of the reinforcing member 120 to the groove structure is in the range of 0.25 to 4, and the ratio β of the lateral area of ​​the reinforcing member 120 to the groove structure is in the range of 0.2 to 0.7. In some embodiments, by adjusting the number of the annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness H of the diaphragm of each openwork area i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 100 to 1000. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 10, and the lateral area ratio β of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 0.8.

[0219] As shown in FIG. 28, FIG. 28 is a schematic diagram of a vibrating assembly in which the elongated structure of the inner ring and the elongated structure of the outer ring are discontinuous, according to some embodiments herein. In some embodiments, when the vibrating assembly 100 includes at least two annular structures, the annular structure 122 divides the elongated structure 124 into a plurality of regions along the extension direction from the center to the periphery, and the elongated structure 124 in each region may be disposed continuously or discontinuously. In some embodiments, the annular structure 122 may include a first annular structure 1221 and a second annular structure 1222 whose centers of gravity overlap, and the radial dimension of the first annular structure 1221 is smaller than the radial dimension of the second annular structure 1222. The elongated structure 124 may include at least one first elongated structure 1241 and at least one second elongated structure 1242, where the at least one first elongated structure 1241 is disposed inside and connected to the first annular structure 1221, and the at least one second elongated structure 1242 is disposed between and connected to the first annular structure 1221 and the second annular structure 1222. In some embodiments, the at least one first elongated structure 1241 and the at least one second elongated structure 1242 may be connected to the first annular structure 1221 at different positions. In some embodiments, the first elongated structures 1241 and the second elongated structures 1242 may be the same in number or different in number.

[0220] By discontinuously arranging the elongated structures 124 in the inner and outer regions of the annular structure 122, it is possible to realize different numbers of the elongated structures 124 in the inner and outer regions of the annular structure 122, different lateral widths of the elongated structures 124 in the inner and outer regions, and different lateral shapes of the elongated structures 124 in the inner and outer regions, thereby making it possible to adjust the mass, stiffness and center of mass distribution of the reinforcing member 120 and the number and area of ​​the openwork regions in the central region 112 over a wide range.

[0221] In some embodiments, adjusting the mass of the stiffening member 120 can adjust and change the total equivalent mass Mt, thereby changing the resonant frequency of the resulting mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibrating assembly 100. By adjusting the stiffness of the stiffening member 120, the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 The resonant frequency of the system's inversion motion can be adjusted, thereby changing the second resonant position of the vibrating assembly 100, and the second resonant peak of the vibrating assembly 100 can be adjusted with a 3 dB bandwidth by making the stiffness distribution different at different positions extending from the center to the periphery of the elongated structure 124. The third resonant peak position and sensitivity of the vibrating assembly 100 can be changed by adjusting the number and area of ​​the openwork regions in the central region 112.

[0222] In some embodiments, by distributing the elongated structures 124 in the inner and outer regions of the annular structure 122 discontinuously, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork region. i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 150 to 700. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the transverse area ratio β of the reinforcing member 120 to the groove structure is in the range of 0.25 to 4. In some embodiments, by distributing the elongated structures 124 in the inner and outer regions of the annular structure 122 discontinuously, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm of each openwork area i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 100 to 1000. ki and S. jiThe ratio γ of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 10, and the lateral area ratio β of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 0.8.

[0223] As shown in Fig. 29, Fig. 29 is a schematic diagram of a vibration assembly having multiple annular structures, according to some embodiments of the present disclosure. In some embodiments, the multiple annular structures 122 can be designed to design the spacing regions of the multiple annular structures 122, and the number of elongated structures 124 in different spacing regions can be designed to design the mass distribution of the stiffening member 120. Note that the elongated structures 124 designed for the spacing regions of each annular structure 122 may be different in number, shape, and position.

[0224] In some embodiments, the annular structures 122 from the center outward are defined as the first annular structure 1221, the second annular structure 1222, the third annular structure 1223, ... the nth annular structure, and the elongated structures 124 in the interval region between the nth annular structure and the n-1th annular structure are defined as the nth elongated structures (e.g., the first elongated structure 1241, the second elongated structure 1242, the third elongated structure 1243), and the number of the nth elongated structures is Q n The physical quantity q can be defined as the number Q of any i-th long-shaped structure. i and the number of j-th long structures Q j It is defined as the ratio of

[0225] q=Q i / Q j (Formula 11)

[0226] In some embodiments, the number Q of any i-th elongated structure may be i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number i of elongated structures Q may range from 0.05 to 20. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number i of elongated structures Q may range from 0.1 to 10. i and the number of j-th long structures Qj The ratio q of the number of any i-th elongated structure to the number of scallops may range from 0.1 to 8. i and the number of j-th long structures Q j The ratio q of the number of any i-th elongated structure to the number of scallops may range from 0.1 to 6. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number i of elongated structures Q may range from 0.5 to 6. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number i of elongated structures Q may range from 1 to 4. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number i of elongated structures Q may range from 1 to 2. i and the number of j-th long structures Q j The ratio q may be in the range of 0.5 to 2.

[0227] In some embodiments, the shape of the annular structure 122 may include at least one of a circular annular shape, an elliptical annular shape, a polygonal annular shape, and a curved annular shape. By designing the annular structures 122 with different shapes and / or different dimensions, the mass, stiffness of the reinforcing member 120 can be adjusted, and the area of ​​the openwork region of the central region 112 can be adjusted.

[0228] In some embodiments, the relationship between the size of the suspension region 1121 and the area of ​​the central region 112 allows the reinforcing member 120 to undergo a constant bending deformation in the frequency band, realizing the enhancement and cancellation of the sound pressures of different regions of the elastic element 110 due to the superposition of the sound pressures, thereby realizing the maximum sound pressure level output. v and the horizontal projection area S of the center of the vibration membrane of the vibration assembly 100 c Compared to,

[0229]

number

[0230] may be in the range of 0.05 to 0.7. In some embodiments, the horizontal plane projection area S of the suspension region 1121 v and the horizontal projection area S of the center of the vibration membrane of the vibration assembly 100 c Compared to,

[0231]

number

[0232] may be in the range of 0.1 to 0.5. In some embodiments, the horizontal plane projection area S of the suspension region 1121 v and the horizontal projection area S of the center of the vibration membrane of the vibration assembly 100 c Compared to,

[0233]

number

[0234] may be in the range of 0.15 to 0.35.

[0235] 30A-30E, which are schematic diagrams of vibration assemblies having different structures according to some embodiments herein. In some embodiments, the outer contour of the reinforcing member 120 may be a structure having outwardly extending spokes (as shown in FIG. 30A), a circular ring structure, an elliptical ring structure, or a curved ring structure (as shown in FIG. 30B), a polygon, other irregular ring structure, etc., where the polygon may include a triangle, a square, a pentagon, a hexagon (as shown in FIGS. 30C and 30D), a heptagon, an octagon, a nonagon, a decagon, etc. In some embodiments, the elastic element 110 may be a polygon, such as a triangle, a square (as shown in FIGS. 30D and 30E ), a pentagon, a hexagon, a heptagon, an octagon, a nonagon, a decagon, etc., and other irregular shapes, and accordingly, the reinforcing member 120 may be designed to be of similar or dissimilar structure, thereby controlling the shape of the suspension region 1121 by the shape of the edges of the reinforcing member 120, the central region 112, and the edge region 114 to achieve tuning of the performance of the vibrating assembly 100.

[0236] As shown in FIG. 31, FIG. 31 is a schematic diagram of a vibration assembly with annular structures of unequal widths according to some embodiments herein. In some embodiments, by designing local structures of unequal widths at different positions of any of the annular structures 122, the mass of the stiffening member 120 can be effectively adjusted, and the total equivalent mass Mt can be adjusted and changed, so that the resonant frequency of the formed mass Mt-spring Kt-damping Rt system is changed, and the primary resonant frequency of the vibration assembly 100 is further changed. And by designing local structures of unequal widths at different positions (e.g., adjacent positions) of any of the annular structures 122, the stiffness and center of mass distribution of the stiffening member 120 can be adjusted, and the total equivalent mass Mt can be adjusted and changed. 1 -Spring Kt 1 -Attenuation Rt 1The resonant frequency of the system's inversion motion is adjusted to change the second resonant position of the vibrating assembly 100. The design of the unequal width annular structure 122 further provides different stiffness distributions at different positions extending from the center to the periphery of the elongated structure 124, resulting in a second resonant peak of the vibrating assembly 100 that is adjustable in 3 dB bandwidth. The design of the unequal width annular structure 122 also allows the number and area of ​​suspension regions in the central region 112 to be adjusted to change the third resonant peak position and sensitivity of the vibrating assembly 100.

[0237] In some embodiments, by designing a local structure of unequal width at any position (e.g., adjacent positions) of any of the annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork region. i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 150 to 700. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the lateral area ratio β of the reinforcing member 120 to the groove structure is in the range of 0.25 to 4, and the ratio β of the lateral area of ​​the reinforcing member 120 to the groove structure is in the range of 0.2 to 0.7. In some embodiments, by designing a local structure with unequal width at any position of any of the annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm of each openwork area i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 100 to 1000. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 10, and the lateral area ratio β of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 0.8.

[0238] As shown in FIG. 32, FIG. 32 is a schematic diagram of a vibration assembly having an irregular annular structure according to some embodiments of the present specification. In some embodiments, by designing local structures at different positions of different annular structures 122, such as circular, rectangular, square, triangular, hexagonal, octagonal, other polygonal, elliptical annular structures and other irregular annular structures 122, the size, position and shape of the local area of ​​the annular structure 122 can be more flexibly controlled, and the mass of the stiffening member 120 can be effectively adjusted and the total equivalent mass Mt can be adjusted and changed, so that the resonant frequency of the formed mass Mt-spring Kt-damping Rt system is changed, and the first resonant frequency of the vibration assembly 100 is further changed. By adjusting the stiffness of the stiffening member 120 and the distribution of the center of mass of the stiffening member 120, the mass Mt can be adjusted and changed. 1 -Spring Kt 1 -Attenuation Rt 1 The resonant frequency of the system's inversion motion can be adjusted, which changes the second resonant peak position of the vibrating assembly 100, and the stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124 is different, resulting in the second resonant peak of the vibrating assembly 100 adjustable in 3 dB bandwidth. And the third resonant peak position and sensitivity of the vibrating assembly 100 can be changed by effectively adjusting the number and area of ​​the suspension regions of the central region 112. And the irregular structure can be designed to effectively avoid stress concentration, making the deformation of the stiffening member 120 smaller.

[0239] In some embodiments, as shown in FIG. 32 , the reinforcing member 120 includes a double annular structure, which includes an inner first annular structure 1221 and an outer second annular structure 1222. In some embodiments, the first annular structure 1221 and the second annular structure 1222 may have different shapes. In some embodiments, the first annular structure 1221 may be a curved annular structure, and the second annular structure 1222 may be a circular annular structure. In some embodiments, by designing the irregular annular structure 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm of each openwork areai The area-thickness ratio μ, which is the ratio of the area of ​​the openwork region of any two diaphragms, is in the range of 150 to 700. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the transverse area ratio β of the reinforcing member 120 is in the range of 0.25 to 4. In some embodiments, by designing the irregular annular structure 122, the third resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm of each openwork area i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 100 to 1000. ki and S. ji The ratio γ of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 10, and the lateral area ratio β of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 0.8.

[0240] As shown in Fig. 33A-33B, Fig. 33A is a schematic diagram of a vibration assembly including a long-shaped structure with a stepped structure according to some embodiments of the present specification. Fig. 33B is a schematic diagram of a vibration assembly including a long-shaped structure with a stepped structure according to another some embodiments of the present specification. In some embodiments, as shown in Fig. 33A, by designing a reinforcing member 120 including a long-shaped structure 124 with a stepped structure, it can ensure that the stiffness, mass, and mass center distribution of the reinforcing member 120 are changed when the openwork area (affecting the third resonance peak of the vibration assembly 100) and the suspension area 1121 of the central area 112 are not changed by controlling, thereby realizing the effective adjustment of the first resonance peak position, the second resonance peak position and the bandwidth of the vibration assembly 100 when the third resonance peak of the vibration assembly 100 is not changed, and can adjust different frequency response curves according to actual application needs.

[0241] In some embodiments, the thickness of different regions of the stiffening member 120 in the thickness direction (i.e., along the vibration direction of the vibrating assembly 100) can be designed to change the stiffness of the stiffening member 120 itself while keeping the mass of the stiffening member 120 unchanged or changed according to the actual required mass distribution, thereby realizing the stiffness Kt provided to the system by the stiffening member 120 and the elastic element 110. 1 changes, and the mass Mt 1 -Spring Kt 1 -Attenuation Rt 1 The resonant frequency of the reversal motion of the system is changed, which changes the position of the second resonant peak of the vibrating assembly 100, and further allows the 3 dB bandwidth of the second resonant peak of the vibrating assembly 100 to be controlled.

[0242] 33B shows the structure of a reinforcing member 120 having a step-shaped elongated structure 124 and its cross-sectional structure in the DD cross section. The thickness of the outermost step in the structure of the reinforcing member 120 is defined as h1, the thickness of the step most inward from the edge as h2..., and the thickness of the central step as hn, and the physical quantity ε is defined as the ratio between the thicknesses of any two steps hj and hk (k>j).

[0243] ε=hj / hk (Equation 12)

[0244] The physical quantity φ is defined as the ratio of the thickness h1 of the outermost step in the structure of the reinforcing member 120 to the thickness hn of the central step.

[0245] φ=h1 / hn (Eq. 13)

[0246] In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 10. In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 8. In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.2 to 8. In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 7. In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 6. In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.2 to 6. In some embodiments, in order to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.2 to 5.

[0247] In response to the frequency response of some vibration assemblies 100 requiring a low Q value and a wide bandwidth, the reinforcing member 120 can be designed to have a large mass concentrated near the center. In some embodiments, in order to increase the mass of the central region of the reinforcing member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the reinforcing member 120 and the thickness hn of the central step is in the range of 0.1 to 1. In some embodiments, in order to increase the mass of the central region of the reinforcing member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the reinforcing member 120 and the thickness hn of the central step is in the range of 0.2 to 0.8. In some embodiments, in order to increase the mass of the central region of the reinforcing member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the reinforcing member 120 and the thickness hn of the central step is in the range of 0.2 to 0.6. In some embodiments, in order to increase the mass of the central region of the reinforcing member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the reinforcing member 120 and the thickness hn of the central step is in the range of 0.2 to 0.4.

[0248] In response to some vibration assemblies 100 requiring high Q and narrow bandwidth frequency response, the stiffening member 120 may be designed to have a large mass concentrated at the edge region. In some embodiments, in order to increase the mass of the edge region of the stiffening member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the stiffening member 120 and the thickness hn of the central step is in the range of 1 to 10. In some embodiments, in order to increase the mass of the edge region of the stiffening member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the stiffening member 120 and the thickness hn of the central step is in the range of 1.2 to 6. In some embodiments, in order to increase the mass of the edge region of the stiffening member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the stiffening member 120 and the thickness hn of the central step is in the range of 2 to 6. In some embodiments, in order to increase the mass of the edge region of the stiffening member 120, the ratio φ between the thickness h1 of the most peripheral step of the structure of the stiffening member 120 and the thickness hn of the central step is in the range of 3 to 6. In some embodiments, in order to increase the mass of the edge regions of the reinforcing member 120, the ratio φ of the thickness h1 of the most peripheral step in the structure of the reinforcing member 120 to the thickness hn of the central step is in the range of 4 to 6. In some embodiments, in order to increase the mass of the edge regions of the reinforcing member 120, the ratio φ of the thickness h1 of the most peripheral step in the structure of the reinforcing member 120 to the thickness hn of the central step is in the range of 5 to 6.

[0249] As shown in FIG. 34A-C, FIG. 34A-C are schematic diagrams of vibration assemblies having different shapes of reinforcing members according to some embodiments herein. The shape of the reinforcing member 120 in FIG. 34A is rectangular, the annular structure 122 is a single annular rectangular structure, and the elongated structure 124 is a trapezoidal structure. The shape of the reinforcing member 120 in FIG. 34B is rectangular, the annular structure 122 is a double annular rectangular structure, and the elongated structure 124 is a trapezoidal structure. The shape of the reinforcing member 120 in FIG. 34C is hexagonal, the annular structure 122 is a single annular hexagonal structure, and the elongated structure 124 is a trapezoidal structure. In some embodiments, the shape of the reinforcing member 120 of the vibration assembly 100 may match the shape of the elastic element 110. The structure of the elastic element 110 may have various shapes, such as, for example, a circular shape, a square shape, a polygonal shape, and the like. The shape of the corresponding reinforcing member 120 may be designed in different shapes, including, but not limited to, circles, rectangles (e.g., rectangles, squares), triangles, hexagons, octagons, other polygons, ellipses, and other irregular structures.

[0250] The resonant frequency of the vibrating assembly 100 can be changed by flexibly designing different shapes of the reinforcing member 120 and different shapes of the elastic element 110 to change the mass and stiffness of the reinforcing member 120 and the mass and stiffness of the vibrating assembly 100, etc.

[0251] In some embodiments, the shape of the reinforcing member 120 and the shape of the elastic element 110 may both include a number of different shapes, where the elongated structures 124 extending from the central region 112 to the periphery may be designed with different lateral widths, different lateral shapes, and / or the annular structures 122 may be designed with different shapes, numbers, and sizes, and the annular structures 122 may be designed to be generally annular or locally annular. The different annular structures 122 divide the elongated structure 124 into different regions, where the elongated structures 124 in the different regions from the center to the periphery may be continuous, intersecting, equal in number, or unequal. In some embodiments, the annular structures 122 may be designed to be circular, rectangular (e.g., rectangular, square), triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregular shaped structures.

[0252] In some embodiments, by designing the vibrating assembly 100 to include the reinforcing members 120 of different shapes, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork region. i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 150 to 700. ki and S. ji The ratio γ of the groove structure to the lateral area ratio β of the reinforcing member 120 is in the range of 0.25 to 4, and the ratio of the groove structure to the lateral area ratio β of the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the vibrating assembly 100 including the reinforcing member 120 with different shapes, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork region. i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 100 to 1000. ki and S. ji The ratio γ of the area of ​​the groove structure to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the area of ​​the groove structure to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0253] As shown in Figures 35A-35D, Figures 35A-35D are schematic diagrams of a vibration assembly including a localized mass structure according to some embodiments herein. Figure 35A shows a double elastically connected localized mass structure 126, Figure 35B shows a quadruple elastically connected localized mass structure 126, Figure 35C shows an S-shaped quadruple elastically connected localized mass structure 126, and Figure 35D shows an irregular S-shaped quadruple elastically connected localized mass structure 126. In some embodiments, the localized mass structure 126 is designed in the suspension region of the central region 112 to increase the equivalent mass Mm of each openwork region. i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i By flexibly adjusting the stiffness of the stiffening member 120, the third resonance peak of the vibration assembly 100 can be effectively adjusted. And by designing the local mass structure 126, the mass and stiffness of the stiffening member 120 can be further adjusted in a wide range to adjust the first resonance peak and the second resonance peak of the vibration assembly 100.

[0254] In some embodiments, a localized mass structure 126 may be circumferentially connected to an adjacent elongated structure 124 by a dual elastic structure (as shown in FIG. 35A ) or may be circumferentially connected to an adjacent annular structure 122 by a dual elastic structure. In other embodiments, each localized mass structure 126 may not be connected to either an elongated structure 124 or annular structure 122, but only to the elastic element 110.

[0255] In some embodiments, the localized mass structure 126 may be connected to both the adjacent elongated structure 124 and the annular structure 122 by a four-fold elastic structure (shown in FIG. 35B). In some embodiments, the planar shape of the elastic structure may be a regular shape (shown in FIGS. 35A and 35B) or an irregular shape (shown in FIG. 35C). In some embodiments, the localized mass structure 126 may have a regular shape (shown in FIGS. 35A-35C) or any irregular shape (shown in FIG. 35D).

[0256] In some embodiments, by designing the dimensions, location, number, and shape of the local mass structures 126 and the dimensions, location, number, and shape of the elastically connected structures, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork region. i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 150 to 700. ki and S. ji The ratio γ of the groove structure to the reinforcing member 120 in the transverse direction is in the range of 0.25 to 4, and the ratio β of the groove structure to the reinforcing member 120 in the transverse direction is in the range of 0.2 to 0.7. In some embodiments, by designing the size, location, number, and shape of the local mass structure 126 and the size, location, number, and shape of the elastically connected structures, the third resonant peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork region. i The area-thickness ratio μ, which is the ratio of the openwork area S of any two elastic elements 110, is in the range of 100 to 1000. ki and S. ji The ratio γ of the area of ​​the groove structure to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the area of ​​the groove structure to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0257] Although the basic concept has been described above, it is clear to those skilled in the art that the detailed disclosure above is merely provided as an example and does not limit the present application. Although not explicitly described herein, those skilled in the art can make various changes, improvements and modifications to the present application. These changes, improvements and modifications are intended to be suggested by the present application and therefore still fall within the spirit and scope of the exemplary embodiments of the present application.

[0258] Also, certain terms are used herein to describe embodiments of the present application. For example, "one embodiment," "an embodiment," and / or "some embodiments" refer to a particular feature, structure, or characteristic associated with at least one embodiment of the present application. Thus, it is emphasized and understood that references to "one embodiment" or "one embodiment" or "one alternative embodiment" more than once in various parts of this specification do not necessarily all refer to the same embodiment. Also, certain features, structures, or characteristics in one or more embodiments of the present application may be combined as appropriate.

[0259] Additionally, unless expressly recited in the claims, the recitation order of process elements or sequences described herein, the use of alphanumeric characters, or the use of other designations, are not intended to limit the order of steps and methods of the present application. While the above disclosure has set forth through various examples what are presently believed to be various useful embodiments of the invention, it is to be understood that such details are merely illustrative and that the appended claims are not limited to only the disclosed embodiments, but on the contrary are intended to cover all modifications and equivalent combinations that are within the spirit and scope of the embodiments of the present application.

[0260] Similarly, in the foregoing description of embodiments of the present application, it should be understood that various features may be grouped together in a single embodiment, figure, or description for the purpose of simplifying the description of the present disclosure and facilitating an understanding of one or more embodiments of the present invention. However, this method of disclosure should not be interpreted as reflecting an intention that the subject matter requires more features than are recited in each claim. In fact, an embodiment may include fewer than all features of a single embodiment disclosed above.

[0261] In some embodiments, numbers describing the number of components and attributes are used, and it is understood that the numbers describing such embodiments are modified in some instances by the modifiers "about," "approximately," or "generally." Unless otherwise specified, "about," "approximately," or "generally" indicate that the numbers are allowed to vary by ±20%. Thus, in some embodiments, all numerical parameters used in the specification and claims are approximations that may vary depending on the characteristics required for a particular embodiment. In some embodiments, the numerical parameters should be applied with the stated number of significant digits and ordinary rounding techniques. In some embodiments, the numerical ranges and parameters determining the ranges are approximations; however, in specific embodiments, such numerical values ​​are set as precisely as possible.

[0262] Finally, it should be understood that the embodiments described herein are merely illustrative of the principles of the embodiments of the present application. Other variations are possible within the scope of the present application. Thus, by way of example, and not of limitation, alternative configurations of the embodiments of the present application may be considered consistent with the teachings of the present application. Thus, the embodiments of the present application are not limited to the embodiments expressly introduced and described herein. [Explanation of symbols]

[0263] 100 Vibration Assembly 110 Elastic element 112 Central area 114 Edge Area 116 Fixed area 120 Reinforcement member 121 Groove structure 122 Ring Structure 124 Long structure

Claims

1. A vibration assembly comprising an elastic element including a central region, an edge region disposed on an outer periphery of the central region, and a fixed region disposed on an outer periphery of the edge region, the elastic element being configured to vibrate along a direction perpendicular to the central region, the central region including an elastic member and a reinforcing member stacked along a vibration direction, the reinforcing member having a plurality of groove structures with openings facing the elastic member.

2. The vibrating assembly of claim 1 , wherein the reinforcing member has an openwork structure in an area other than the plurality of groove structures.

3. 3. The vibration assembly according to claim 2, wherein a ratio of a projected area of ​​the reinforcing member to a projected area of ​​the central region in the vibration direction is in a range of 0.15 to 0.

8.

4. 4. The vibration assembly according to claim 3, wherein a ratio of a projected area of ​​the reinforcing member to a projected area of ​​the central region in the vibration direction is in a range of 0.35 to 0.

65.

5. The vibration assembly according to any one of claims 2 to 4, which, when vibrated, exhibits a resonance peak in the range of at least 10,000 Hz to 20,000 Hz.

6. The vibration assembly of any one of claims 1 to 5, wherein the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in the range of 7.14 or more.

7. The vibratory assembly of claim 6 , wherein the ratio of the height dimension to the thickness dimension is in the range of 9 or greater.

8. 8. The vibration assembly according to claim 6 or 7, which, when vibrated, exhibits a resonance peak in the range of at least 5000 Hz to 10000 Hz.

9. The vibration assembly according to any one of claims 1 to 8, wherein the groove structure has a height dimension along the vibration direction, the value of the height dimension being in the range of 50 μm to 500 μm.

10. The vibratory assembly of claim 9, wherein the height dimension has a value in the range of 200 μm to 350 μm.

11. The vibration assembly according to any one of claims 1 to 10, wherein the sidewalls of the groove structure have a thickness dimension, the value of the thickness dimension being in the range of 50 μm or less.

12. The vibratory assembly of claim 11 , wherein the thickness dimension has a value in the range of 40 μm or less.

13. A vibration assembly according to any one of claims 1 to 12, wherein an opening of the groove structure is provided with a skirt structure extending along a surface of the elastic member, the skirt structure having a width in the range of 100 μm to 300 μm.

14. The vibratory assembly of claim 13, wherein the width of the skirt structure is in the range of 100 μm to 200 μm.

15. The vibration assembly according to any one of claims 1 to 14, wherein the shape of the groove structure includes at least one of a U-shape, a T-shape, an H-shape, and a cone-shape.

16. The vibration assembly according to any one of the preceding claims, wherein the Young's modulus of the material of the reinforcing member is higher than the Young's modulus of the material of the elastic member.

17. The vibrating assembly according to any one of the preceding claims, wherein the material of the reinforcing member is the same as the material of the elastic member.

18. The vibration assembly according to any one of claims 1 to 17, wherein a filler material is disposed in the groove structure, the Young's modulus of the filler material being smaller than the Young's modulus of the material of the reinforcing member.

19. A vibration assembly comprising an elastic element including a central region, an edge region disposed on an outer periphery of the central region, and a fixing region disposed on an outer periphery of the edge region, the elastic element being configured to vibrate along a direction perpendicular to the central region, the central region including a reinforcing region and an elastic region arranged in parallel, the reinforcing region having a plurality of groove structures with openings facing in the vibration direction.

20. 20. The vibration assembly according to claim 19, wherein in the vibration direction, a ratio between a projected area of ​​the reinforced region and a projected area of ​​the central region is in a range of 0.15 to 0.

8.

21. 21. The vibration assembly according to claim 20, wherein in the vibration direction, a ratio between a projected area of ​​the reinforced region and a projected area of ​​the central region is in a range of 0.35 to 0.

65.

22. 22. The vibration assembly according to claim 20 or 21, which when vibrated exhibits a resonant peak in the range of at least 10,000 Hz to 20,000 Hz.

23. 23. The vibration assembly of claim 19, wherein the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in the range of 7.14 or more.

24. 24. The vibratory assembly of claim 23, wherein the ratio of the height dimension to the thickness dimension is in the range of 9 or greater.

25. 25. The vibration assembly according to claim 23 or 24, which when vibrated exhibits a resonant peak in the range of at least 5000 Hz to 10000 Hz.

26. The vibration assembly according to any one of claims 19 to 25, wherein the groove structure has a height dimension along the vibration direction, the value of the height dimension being in the range of 50 μm to 500 μm.

27. 27. The vibratory assembly of claim 26, wherein the height dimension has a value in the range of 200 μm to 350 μm.

28. The vibration assembly of any one of claims 19 to 26, wherein a sidewall of the groove structure has a thickness dimension, the thickness dimension having a value in the range of 50 μm or less.

29. 30. The vibratory assembly of claim 28, wherein the thickness dimension has a value in the range of 40 μm or less.

30. 30. The vibration assembly according to any one of claims 19 to 29, wherein an opening of the groove structure is provided with a skirt structure connected to the elastic region, the skirt structure having a width in the range of 100 μm to 300 μm.

31. The vibratory assembly of claim 30, wherein the skirt structure has a width in the range of 100 μm to 200 μm.

32. The vibration assembly of any one of claims 19 to 31, wherein the shape of the groove structure includes at least one of a U-shape, a T-shape, an L-shape, and a cone-shape.

33. A vibration assembly according to any one of claims 19 to 32, wherein the Young's modulus of the material of the reinforced region is higher than the Young's modulus of the material of the elastic region.

34. A vibration assembly according to any one of claims 19 to 32, wherein the material of the reinforced region is the same as the material of the elastic region.

35. The vibration assembly according to any one of claims 19 to 34, wherein a filling material is provided in the groove structure, the Young's modulus of the filling material being smaller than the Young's modulus of the material of the elastic element.

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